JP2015129475A - Electric compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an electric compressor that can smooth the flow of a refrigerant toward injection ports through reed valves and reduces a dead volume formed between the reed valves and the injection ports with a simple structure.SOLUTION: A bulge part 35 that protrudes toward end parts of reed valves 42v is provided between respective supply passages 34 in a housing concave part 31. Intermediate-pressure refrigerant gas that flows through a second chamber 31b is guided to the respective supply passages 34 by a side surface part 35a of the bulge part 35.

Description

  The present invention relates to an electric compressor provided with an injection port for introducing an intermediate pressure refrigerant into a compression chamber.

  In general, an injection pipe constituting a part of the external refrigerant circuit is connected to the injection port, and a gas-liquid separator is connected to the injection pipe. The injection piping is provided with a check valve. The check valve opens the injection pipe during high load operation such as heating operation of the refrigeration cycle, and closes the injection pipe during low load operation such as cooling operation. During high load operation of the refrigeration cycle, the check valve opens the injection pipe, and the intermediate-pressure gas refrigerant separated by the gas-liquid separator is introduced into the compression chamber via the injection pipe and the injection port. . Thereby, the flow rate of the gas refrigerant introduced into the compression chamber is increased, and the performance of the electric compressor during high load operation of the refrigeration cycle is improved.

  By the way, in order to further improve the performance of the electric compressor during high load operation of the refrigeration cycle, it is only necessary to increase the flow rate of the gas refrigerant introduced from the injection port into the compression chamber. Can be considered. However, for example, in the case of a scroll-type electric compressor, when the injection port is increased, the spiral wall of the movable scroll moves based on the revolving motion of the movable scroll, and the injection port and the spiral wall of the movable scroll overlap. In addition, adjacent compression chambers may communicate with each other through the injection port across the compression chambers adjacent to each other. Then, the refrigerant leaks from the high pressure side compression chamber to the low pressure side compression chamber, and the performance of the electric compressor is deteriorated.

  Therefore, it is a common practice to provide a plurality of injection ports so that adjacent compression chambers do not communicate with each other via the injection port even if the scroll wall of the movable scroll moves. . By doing so, compared to the case where only one injection port is provided, the flow rate of the gas refrigerant introduced into the compression chamber is increased, and the performance of the electric compressor is further improved during high-load operation of the refrigeration cycle. To do.

  Further, a valve mechanism is provided on the injection piping side of the injection port to prevent the refrigerant that has flowed from the compression chamber through the injection port from flowing back to the injection piping side. As a valve mechanism, for example, a valve mechanism including a spool valve and a coil spring that urges the spool valve to a closed position where the injection port and the injection piping side are not in communication is known (for example, a patent) Reference 1).

  When the pressure of the intermediate-pressure gas refrigerant from the injection piping side acts, the spool valve moves to a valve-opening position that allows the injection port and the injection piping side to communicate against the urging force of the coil spring. Thereby, the gas refrigerant is introduced into the compression chamber via the injection pipe and the injection port. Further, when the intermediate pressure of the gas refrigerant from the injection piping side does not act on the spool valve, the spool valve returns to the closed position by the biasing force of the coil spring. This prevents the refrigerant that has flowed from the compression chamber through the injection port from flowing backward to the injection piping side.

  However, since the spool valve is configured to reciprocate between the valve opening position and the valve closing position based on the relationship between the biasing force of the coil spring and the pressure of the intermediate-pressure gas refrigerant from the injection piping side, the responsiveness is poor. That is, it is difficult to introduce the gas refrigerant into the compression chamber via the injection pipe and the injection port, or the reverse flow from the compression chamber to the injection pipe side in the refrigerant flowing through the injection port. It is likely to occur. Therefore, it is difficult to improve the performance of the electric compressor during high load operation of the refrigeration cycle.

  Therefore, Patent Document 2 discloses a valve mechanism including a reed valve and a retainer forming plate having a retainer that regulates the opening degree of the reed valve. The reed valve opens when the intermediate pressure of the gas refrigerant from the injection piping side acts. At this time, the opening degree of the reed valve is restricted by contacting the retainer. Thereby, the gas refrigerant is introduced into the compression chamber via the injection pipe and the injection port. The reed valve closes when the intermediate pressure gas refrigerant pressure from the injection piping side stops working. This prevents the refrigerant that has flowed from the compression chamber through the injection port from flowing backward to the injection piping side.

  Therefore, the reed valve is more responsive than a spool valve that is configured to reciprocate between the valve opening position and the valve closing position because of the relationship between the biasing force of the coil spring and the pressure of the intermediate-pressure gas refrigerant from the injection piping side. Therefore, the performance of the electric compressor becomes good during high load operation of the refrigeration cycle.

JP-A-8-303361 JP-A-11-107945

  By the way, if the gas refrigerant passing through the reed valve from the injection pipe and going to the injection port does not flow smoothly toward the injection port, the gas refrigerant is not efficiently introduced into the compression chamber through the injection port, and the refrigeration is performed. It is difficult to improve the performance of the electric compressor during high-load operation of the cycle. Further, the space between the reed valve and the injection port is a dead volume. As the dead volume increases, the gas refrigerant re-expands and the performance of the electric compressor deteriorates.

  The present invention has been made in order to solve the above-mentioned problems, and the object thereof is to smooth the flow of the refrigerant passing through the reed valve and going to the injection port, and from the reed valve to the injection port. Another object of the present invention is to provide an electric compressor capable of reducing the dead volume formed between the two with a simple configuration.

  An electric compressor that solves the above problems includes an electric motor and a suction housing that includes a compression mechanism that compresses the refrigerant sucked by rotation of the electric motor, and a refrigerant compressed in a compression chamber formed in the compression mechanism. A discharge housing having a discharge chamber from which the refrigerant is discharged, and the suction housing has an intermediate pressure refrigerant higher than the suction pressure of the sucked refrigerant and lower than the discharge pressure of the discharged refrigerant, An electric compressor provided with a plurality of injection ports to be introduced into the compression chamber in the middle of compression from an external refrigerant circuit, wherein the electric compressor introduces the intermediate pressure refrigerant from the external refrigerant circuit, and communicates with the introduction port An intermediate pressure housing, and a plurality of supply passages communicating the storage recess and the injection port. A valve forming member that is disposed between the suction housing and the discharge housing, and that includes a valve hole and a reed valve that opens and closes the valve hole, is housed in the housing recess. The plurality of fastening portions are fastened to the intermediate pressure housing, and at the bottom of the housing recess, openings of the plurality of supply passages are formed at positions shifted from the valve holes, and openings of adjacent supply passages are formed. In between, a bulging portion extending toward the valve forming member is formed, and the bulging portion guides the intermediate pressure refrigerant introduced from the valve hole to the opening of the supply passage, respectively. A guide wall to be provided on the side surface, and an upper wall portion facing the valve forming member and to which at least one of the fastening portions is fastened.

  According to this, when the reed valve is opened, intermediate pressure refrigerant is introduced from the external refrigerant circuit into the compression chamber via the introduction port, the accommodating recess, each supply passage, and each injection port. Further, when the reed valve is closed, the refrigerant flowing from the compression chamber to each injection port is prevented from flowing to the introduction port, and the refrigerant is prevented from flowing back to the external refrigerant circuit.

  Further, the intermediate pressure refrigerant introduced from the valve hole is guided to each supply passage by the guide wall of the bulging portion, and flows into each injection port through each supply passage. Therefore, the flow of the refrigerant passing through the reed valve and going to each injection port can be made smooth. Further, by extending the bulging portion toward the valve forming member, the bulging portion is formed between the reed valve and the injection port as compared with the case where the bulging portion does not extend toward the valve forming member. Dead volume can be reduced. That is, since the bulging portion including the upper wall portion to which at least one of the fastening portions is fastened is used, the bulging portion is extended toward the valve forming member only for the purpose of reducing the dead volume. There is no need, and the dead volume formed between the reed valve and the injection port can be reduced with a simple configuration.

In the electric compressor, the guide wall is preferably curved in an arc shape.
According to this, since the intermediate-pressure refrigerant introduced from the valve hole can easily flow along the guide wall, the flow of the refrigerant passing through the reed valve toward each injection port can be further smoothed. it can.

In the electric compressor, it is preferable that the guide wall is disposed at a center between the openings of the adjacent supply passages.
According to this, as compared with the case where the guide wall is disposed at a position close to one of the adjacent supply passages, the intermediate pressure refrigerant introduced from the valve hole by the guide wall is supplied to each supply passage. Can flow evenly.

  According to the present invention, the flow of the refrigerant passing through the reed valve toward the injection port can be made smooth, and the dead volume formed between the reed valve and the injection port can be reduced with a simple configuration. Can do.

A longitudinal section of a scroll type compressor in an embodiment. FIG. 2 is a sectional view taken along line 2-2 in FIG. 1. The top view of an intermediate pressure housing. The exploded perspective view of an intermediate pressure housing, a valve formation member, a gasket, and a lid member. The top view which shows the state by which the retainer formation plate and the reed valve formation plate were assembled | attached to the intermediate pressure housing. The circuit diagram which shows an external refrigerant circuit. The top view which shows the state by which the retainer formation plate and the reed valve formation plate were assembled | attached to the intermediate pressure housing in another embodiment.

  Hereinafter, an embodiment in which the electric compressor is embodied as a scroll compressor will be described with reference to FIGS. The scroll compressor according to the present embodiment is mounted on a vehicle and used for a vehicle air conditioner.

  As shown in FIG. 1, the housing 11 of the scroll compressor 10 is made of a metal material (in this embodiment, made of aluminum). The housing 11 includes a bottomed cylindrical suction housing structure 12 having an opening at one end (the left end in FIG. 1), a block-shaped intermediate pressure housing 13 connected to one end of the suction housing structure 12, and an intermediate It has a block-like discharge housing 14 connected to one end of the pressure housing 13 (left end in FIG. 1). Therefore, the intermediate pressure housing 13 is disposed between the suction housing structure 12 and the discharge housing 14. A suction port 12 h is formed in the suction housing structure 12. A discharge port 14 h is formed in the discharge housing 14. Housed in the suction housing component 12 are a compression mechanism 15 for compressing the refrigerant and an electric motor 16 that is a drive source of the compression mechanism 15.

  A shaft support member 17 is fixed near the opening of the suction housing component 12. An insertion hole 17 h is formed at the center of the shaft support member 17. The shaft support member 17 and the suction housing component 12 define a motor chamber 12a in which the electric motor 16 is accommodated. A rotating shaft 18 is accommodated in the suction housing component 12. One end side of the rotation shaft 18 (opening side of the suction housing component 12) is inserted into the insertion hole 17h of the shaft support member 17, and is rotatably supported by the shaft support member 17 via the bearing B1. The other end side of the rotating shaft 18 (the bottom wall side of the suction housing component 12) is rotatably supported by the suction housing component 12 via a bearing B2.

  The electric motor 16 includes a rotor 16a (rotor) that rotates integrally with the rotary shaft 18, and a stator 16b (stator) that is fixed to the inner peripheral surface of the suction housing component 12 so as to surround the rotor 16a. Has been.

  The compression mechanism 15 includes a fixed scroll 20 and a movable scroll 21. The fixed scroll 20 includes a disk-shaped fixed substrate 20a and a fixed spiral wall 20b standing from the fixed substrate 20a. The movable scroll 21 includes a movable substrate 21a having a disk shape and a movable spiral wall 21b standing from the movable substrate 21a toward the fixed substrate 20a. In the present embodiment, the suction housing is constituted by the suction housing structure 12 and the fixed substrate 20a.

  An eccentric shaft 18 a protrudes at a position eccentric to the rotation axis L of the rotation shaft 18 on one end surface of the rotation shaft 18. A bush 18b is fitted and fixed to the eccentric shaft 18a. A movable substrate 21a is supported on the bush 18b via a bearing B3 so as to be rotatable relative to the bush 18b.

  The fixed spiral wall 20b and the movable spiral wall 21b are meshed with each other. The distal end surface of the fixed spiral wall 20b is in contact with the movable substrate 21a, and the distal end surface of the movable spiral wall 21b is in contact with the fixed substrate 20a. The compression chamber 22 is partitioned by the fixed substrate 20a and the fixed spiral wall 20b, and the movable substrate 21a and the movable spiral wall 21b. The shaft support member 17 is formed with a suction passage 17a that allows the motor chamber 12a and the compression chamber 22 to communicate with each other.

  A rotation prevention mechanism 23 is disposed between the movable substrate 21 a and the shaft support member 17. The rotation prevention mechanism 23 includes a plurality of annular holes 23a (only one is shown in FIG. 1) provided on the end surface on the movable substrate 21a side of the shaft support member 17, and an outer periphery of the end surface on the shaft support member 17 side of the movable substrate 21a. And a pin 23b which is protruded from the portion and loosely fitted in each annular hole 23a.

  When the rotary shaft 18 is rotationally driven by the electric motor 16, the movable scroll 21 is revolved around the axis of the fixed scroll 20 (rotation axis L of the rotary shaft 18) via the eccentric shaft 18a. At this time, the movable scroll 21 is prevented from rotating by the rotation blocking mechanism 23, and only the revolving motion is allowed. Due to the revolution movement of the movable scroll 21, the volume of the compression chamber 22 decreases.

  A discharge port 20e is formed in the center of the fixed substrate 20a. A discharge valve 20v is attached to the fixed substrate 20a so as to cover the discharge port 20e. In the intermediate pressure housing 13, a communication passage 24 communicating with the discharge port 20e is formed. A discharge chamber 25 communicating with the communication passage 24 is formed in the discharge housing 14. The discharge housing 14 is formed with an oil separation chamber 26 communicating with the discharge port 14h. Further, a passage 27 that communicates the discharge chamber 25 and the oil separation chamber 26 is formed in the discharge housing 14. An oil separation cylinder 28 is provided in the oil separation chamber 26. The oil separation cylinder 28 includes a large-diameter portion 28a fitted in the oil separation chamber 26, and a small-diameter portion 28b below the large-diameter portion 28a and having a smaller diameter than the large-diameter portion 28a.

  As shown in FIG. 2, two injection ports 30 are formed in the fixed substrate 20a. Each injection port 30 has a circular hole shape, and is formed on the fixed substrate 20a so that the adjacent compression chambers 22 do not communicate with each other through the injection port 30 even if the movable scroll 21 revolves. The position and size to be set are set.

  As shown in FIG. 3, an accommodation recess 31 having a substantially rectangular shape in plan view is formed on the end surface of the intermediate pressure housing 13 on the discharge housing 14 side. In addition, the intermediate pressure housing 13 is formed with an introduction port 33 to which an injection pipe 32 (external refrigerant circuit 50) for introducing an intermediate pressure refrigerant into the accommodating recess 31 is connected. The bottom wall of the housing recess 31 has a retainer housing recess 311. The retainer housing recess 311 extends from the central portion of the housing recess 31 toward the inner wall of the housing recess 31 opposite to the introduction port 33.

  Further, the bottom wall of the housing recess 31 is continuous with both corners of the retainer housing recess 311 opposite to the introduction port 33 and extends toward both corners of the housing recess 31 opposite to the introduction port 33. A recess 312 is provided. Furthermore, the bottom wall of the housing recess 31 has a connecting recess 313 that connects the pair of recesses 312 and is formed on the opposite side of the introduction port 33 from the retainer housing recess 311. An opening of a supply passage 34 that communicates with each injection port 30 is formed in the bottom wall of each recess 312. Therefore, the housing recess 31 communicates with each supply passage 34. Each supply passage 34 has a circular hole shape and is formed in the same size as each injection port 30.

  A pair of female screw holes 31 h are formed at both corners on the inner wall side on the introduction port 33 side in the bottom wall of the housing recess 31. Further, between the openings of the supply passages 34 in the bottom wall of the housing recess 31, a bulging portion 35 extending from the inner wall of the housing recess 31 opposite to the introduction port 33 toward the retainer housing recess 311 is formed. Has been. A side surface portion 35a on the side of the retainer accommodating recess 311 in the bulging portion 35 is curved in an arc shape. A female screw hole 35 h is formed in the upper wall portion 35 b on the opening side of the housing recess 31 in the bulging portion 35.

  As shown in FIG. 1, the valve forming member 40 is housed in the housing recess 31. The valve forming member 40 includes a valve plate 41, a reed valve forming plate 42, and a retainer forming plate 43.

  As shown in FIG. 4, the valve plate 41 has a flat plate shape and is made of a metal material (made of iron in the present embodiment), and its outer shape is shaped along the inner wall of the housing recess 31. Two circular valve holes 41 a are formed in the central portion of the valve plate 41. Further, three bolt insertion holes 41 h are formed on the outer peripheral portion of the valve plate 41.

  The reed valve forming plate 42 has a thin plate shape and is made of a metal material (made of iron in this embodiment), and its outer shape is shaped along the inner wall of the housing recess 31. The reed valve forming plate 42 is formed of an outer frame portion 42a and two reed valves 42v projecting from the outer frame portion 42a to the central portion. Each reed valve 42v extends from the outer frame portion 42a to the center portion, and its tip portion is circular in plan view. The leading end of the reed valve 42v is formed in a size that can cover the valve hole 41a. Further, three bolt insertion holes 42h are formed in the outer frame portion 42a.

  The retainer forming plate 43 has a thin flat plate shape and is made of a rubber material, and has an outer shape along the inner wall of the housing recess 31. The retainer forming plate 43 is formed of an outer frame portion 43a and a retainer 43b that projects from the outer frame portion 43a toward the center portion and regulates the opening degree of the reed valve 42v. The retainer 43b is housed in the retainer housing recess 311. Also, three bolt insertion holes 43h are formed in the outer frame portion 43a.

  On the bottom wall of the housing recess 31, a retainer forming plate 43, a reed valve forming plate 42, and a valve plate 41 are arranged in this order. In a state where the retainer forming plate 43, the reed valve forming plate 42, and the valve plate 41 are housed in the housing recess 31, the bolt insertion holes 41h, 42h, and 43h overlap each other. The retainer forming plate 43, the reed valve forming plate 42, and the valve plate 41 have a bolt 45 as a fastening portion inserted into each bolt insertion hole 41h, 42h, 43h in the pair of female screw holes 31h and the female screw holes 35h. By being screwed respectively, it is fastened to the bottom wall of the accommodating recess 31.

  The bottom wall of the housing recess 31 and the bulging portion 35 receive the axial force of the bolt 45. The bulging portion 35 has a predetermined thickness and can receive the fastening force of the bolt 45. Each bolt 45 is disposed so as to surround each reed valve 42v. Each valve hole 41 a is disposed between the supply passages 34. Further, as shown in FIG. 1, the introduction port 33 is located at a position orthogonal to the rotation axis L of the rotation shaft 18 on the inner wall of the housing recess 31 and opens closer to the discharge housing 14 than the valve plate 41. ing.

  The opening of the housing recess 31 is closed by a flat lid member 44. The lid member 44 is fastened to the intermediate pressure housing 13 by a bolt 46 and is disposed inside the discharge chamber 25. Between the lid member 44 and the intermediate pressure housing 13, a part of a gasket 47 that seals between the intermediate pressure housing 13 and the discharge housing 14 is interposed. Therefore, the space between the inside of the housing recess 31 and the discharge chamber 25 is sealed by the gasket 47.

  The interior of the housing recess 31 is partitioned by a valve plate 41 into a first chamber 31a on the introduction port 33 side and a second chamber 31b on the supply passage 34 side. The first chamber 31 a is partitioned by the valve plate 41, the inner wall of the housing recess 31, and the lid member 44. The second chamber 31 b is partitioned by the valve plate 41, a pair of recesses 312, and a connecting recess 313. The space between the first chamber 31 a and the second chamber 31 b is sealed by an outer frame portion 43 a (outer peripheral portion) of the retainer forming plate 43. The seal between the first chamber 31 a and the second chamber 31 b in the outer frame portion 43 a of the retainer forming plate 43 is secured by fastening each bolt 45.

  As shown in FIG. 5, the bulging portion 35 extends toward the tip end portion (valve forming member 40) of each reed valve 42v. Further, the bulging portion 35 is a portion facing between the tip portions of the reed valves 42v in the second chamber 31b, and is disposed at the center between the openings of the supply passages 34. The leading end of each reed valve 42v is arranged near the center connecting each supply passage 34 with a straight line L1 (indicated by a two-dot chain line in FIG. 5). The opening of each supply passage 34 is formed at a position shifted from the valve hole 41a.

  As shown in FIG. 6, the external refrigerant circuit 50 includes a scroll compressor 10, a pipe switching valve 51, a first heat exchanger 52, a second heat exchanger 53, a first expansion valve 54, a second expansion valve 55, and The gas-liquid separator 56 is configured.

  The pipe switching valve 51 has first to fourth ports 51a, 51b, 51c, 51d. And the piping switching valve 51 is in the 1st state (state shown as a continuous line in Drawing 3) which makes the 3rd mouth 51c and the 4th mouth 51d communicate simultaneously with the 1st mouth 51a and the 2nd mouth 51b. The first port 51a and the third port 51c can be communicated with each other, and at the same time, the second port 51b and the fourth port 51d can be switched to a second state (a state indicated by a broken line in FIG. 3). .

  One end of the discharge pipe 57 is connected to the discharge port 14 h, and the other end of the discharge pipe 57 is connected to the first port 51 a of the pipe switching valve 51. One end of the first pipe 58 is connected to the second port 51 b of the pipe switching valve 51, and the other end of the first pipe 58 is connected to the first heat exchanger 52. One end of the second pipe 59 is connected to the first heat exchanger 52, and the other end of the second pipe 59 is connected to the first expansion valve 54.

  One end of a third pipe 60 is connected to the first expansion valve 54, and the other end of the third pipe 60 is connected to a gas-liquid separator 56. One end of the fourth pipe 61 is connected to the gas-liquid separator 56, and the other end of the fourth pipe 61 is connected to the second expansion valve 55. One end of the fifth pipe 62 is connected to the second expansion valve 55, and the other end of the fifth pipe 62 is connected to the second heat exchanger 53. One end of the sixth pipe 63 is connected to the second heat exchanger 53, and the other end of the sixth pipe 63 is connected to the third port 51 c of the pipe switching valve 51. One end of the suction pipe 64 is connected to the fourth port 51d of the pipe switching valve 51, and the other end of the suction pipe 64 is connected to the suction port 12h.

  One end of the injection pipe 32 is connected to the gas-liquid separator 56, and the other end side of the injection pipe 32 is connected to the introduction port 33. A check valve 66 is provided in the injection pipe 32.

Next, the operation of this embodiment will be described.
When the rotor 16a rotates, the movable scroll 21 revolves through the rotating shaft 18. Then, a compression operation and a discharge operation are performed in the compression mechanism 15, and the refrigerant circulates in the external refrigerant circuit 50. Then, the low-pressure refrigerant is sucked into the motor chamber 12a through the suction port 12h. The refrigerant sucked into the motor chamber 12a is sucked into the compression chamber 22 through the suction passage 17a by the turning (suction operation) of the movable scroll 21. The refrigerant in the compression chamber 22 is compressed by the turning (discharging operation) of the movable scroll 21 and pushes the discharge valve 20v out of the discharge port 20e while being compressed, and is discharged to the communication passage 24 as a high-pressure refrigerant. It flows out into the discharge chamber 25.

  The refrigerant in the discharge chamber 25 flows out to the oil separation chamber 26 through the passage 27. The refrigerant flowing into the oil separation chamber 26 swirls around the small diameter portion 28b and then flows into the oil separation cylinder 28 from the lower opening of the small diameter portion 28b. The refrigerant flowing into the oil separation cylinder 28 is discharged to the discharge pipe 57 through the discharge port 14h.

  Lubricating oil is separated from the refrigerant swirled around the small diameter portion 28b. The lubricating oil separated from the refrigerant falls to the lower part of the oil separation chamber 26. A part of the refrigerant in the oil separation chamber 26 and the lubricating oil separated in the oil separation chamber 26 enter the suction housing structure 12 through a supply passage (not shown) formed in the discharge housing 14 and the intermediate pressure housing 13. Supplied and contributes to lubrication of sliding parts such as the compression mechanism 15 and the rotary shaft 18.

  During the cooling operation, the pipe switching valve 51 is switched to the first state in which the first port 51a and the second port 51b are in communication with each other and the third port 51c and the fourth port 51d are in communication. Thereby, the refrigerant discharged to the discharge pipe 57 flows into the first heat exchanger 52 via the first port 51a, the second port 51b, and the first tube 58. The refrigerant that has flowed into the first heat exchanger 52 undergoes heat exchange with the outside air in the first heat exchanger 52 and condenses. The refrigerant condensed in the first heat exchanger 52 flows into the first expansion valve 54 via the second pipe 59. The refrigerant flowing into the first expansion valve 54 is depressurized by the first expansion valve 54 to become an intermediate pressure (intermediate pressure) between the discharge pressure (high pressure) and the suction pressure (low pressure), and the third pipe. It flows into the gas-liquid separator 56 via 60. The refrigerant that has flowed into the gas-liquid separator 56 is separated into a gas refrigerant and a liquid refrigerant by the gas-liquid separator 56.

  The liquid refrigerant separated by the gas-liquid separator 56 flows into the second expansion valve 55 via the fourth pipe 61 and is decompressed by the second expansion valve 55. The liquid refrigerant decompressed by the second expansion valve 55 flows into the second heat exchanger 53 via the fifth pipe 62 and evaporates by being exchanged with the indoor air by the second heat exchanger 53. The indoor air is cooled. The refrigerant evaporated by the second heat exchanger 53 is returned to the motor chamber 12a through the sixth pipe 63, the third port 51c, the fourth port 51d, and the suction pipe 64 and through the suction port 12h.

  The gas refrigerant separated by the gas-liquid separator 56 flows into the injection pipe 32. Here, when the indoor air is cooled (during cooling operation), the temperature and pressure of the refrigerant sucked into the motor chamber 12a are high. For this reason, the check valve 66 closes the injection pipe 32 due to the pressure difference between the scroll compressor 10 side and the gas-liquid separator 56 side. Thereby, the introduction of the gas refrigerant from the injection pipe 32 to the introduction port 33 is regulated.

  During the heating operation, the pipe switching valve 51 is switched to the second state in which the first port 51a and the third port 51c are in communication with each other and the second port 51b and the fourth port 51d are in communication with each other. Thereby, the refrigerant discharged to the discharge pipe 57 flows into the second heat exchanger 53 through the first port 51a, the third port 51c, and the sixth pipe 63. The refrigerant that has flowed into the second heat exchanger 53 undergoes heat exchange with the indoor air in the second heat exchanger 53 and condenses, whereby the indoor air is heated. The refrigerant condensed in the second heat exchanger 53 flows into the second expansion valve 55 via the fifth pipe 62. The refrigerant that has flowed into the second expansion valve 55 is decompressed by the second expansion valve 55, becomes an intermediate pressure that is higher than the suction pressure and lower than the discharge pressure, and passes through the fourth pipe 61 to form a gas-liquid separator. 56. The refrigerant that has flowed into the gas-liquid separator 56 is separated into a gas refrigerant and a liquid refrigerant by the gas-liquid separator 56.

  The liquid refrigerant separated by the gas-liquid separator 56 flows into the first expansion valve 54 via the third pipe 60 and is decompressed by the first expansion valve 54. The liquid refrigerant depressurized by the first expansion valve 54 flows into the first heat exchanger 52 via the second pipe 59 and evaporates by exchanging heat with the outside air in the first heat exchanger 52. The refrigerant evaporated by the first heat exchanger 52 is returned to the motor chamber 12a through the first pipe 58, the second port 51b, the fourth port 51d, and the suction pipe 64 through the suction port 12h.

  The gas refrigerant separated by the gas-liquid separator 56 flows into the injection pipe 32. Here, when indoor air is heated (at the time of heating operation), the temperature and pressure of the refrigerant sucked into the motor chamber 12a are low. For this reason, the check valve 66 opens the injection pipe 32 due to the pressure difference between the scroll compressor 10 side and the gas-liquid separator 56 side. Thereby, the introduction of the gas refrigerant from the injection pipe 32 to the introduction port 33 is allowed.

  When the gas refrigerant is introduced from the injection pipe 32 to the introduction port 33, the gas refrigerant flows into the first chamber 31a and each valve hole 41a, and the pressure of the intermediate-pressure gas refrigerant acts on each reed valve 42v. The valve 42v is opened. At this time, each reed valve 42v is in contact with the retainer 43b and its opening degree is regulated. Thereby, the intermediate-pressure gas refrigerant is transferred from the injection pipe 32 to the compression chamber 22 in the middle of compression through the introduction port 33, the first chamber 31 a, the valve holes 41 a, the second chamber 31 b, the supply passages 34, and the injection ports 30. Is introduced.

  As shown in FIG. 5, the intermediate-pressure gas refrigerant introduced into the second chamber 31 b from each valve hole 41 a is guided to each supply passage 34 by the side surface portion 35 a of the bulging portion 35, and passes through each supply passage 34. And flows into the respective injection ports 30. For this reason, the flow of the intermediate-pressure gas refrigerant passing through the reed valve 42v toward the injection ports 30 becomes smooth. Therefore, the side surface portion 35 a of the bulging portion 35 functions as a guide wall that guides the intermediate-pressure gas refrigerant flowing through the second chamber 31 b to each supply passage 34. Further, by extending the bulging portion 35 toward the tip end portion (valve forming member 40) of the reed valve 42v, the bulging portion 35 is not extended toward the tip end portion of the reed valve 42v. And the dead volume formed in the second chamber 31b is reduced.

  Further, the bulging portion 35 is disposed at the center between the openings of the supply passages 34. According to this, compared with the case where the bulging portion 35 is disposed at a position close to either one of the supply passages 34, the second side from each valve hole 41 a is caused by the side surface portion 35 a of the bulging portion 35. The intermediate-pressure gas refrigerant introduced into the chamber 31 b flows evenly through the supply passages 34.

  Then, by introducing the intermediate-pressure gas refrigerant into the compression chamber 22 in the middle of compression via each injection port 30, the flow rate of the gas refrigerant introduced into the compression chamber 22 increases, resulting in a high load during heating operation. The performance of the scroll compressor 10 during operation is improved.

  Further, each reed valve 42v is closed when the intermediate pressure gas refrigerant pressure from the injection pipe 32 side does not act. Then, the gas refrigerant flowing from the compression chamber 22 to each injection port 30, each supply passage 34, and the second chamber 31b is prevented from flowing to the first chamber 31a via each valve hole 41a, and to the injection pipe 32 side. It is prevented that the gas refrigerant flows backward.

In the above embodiment, the following effects can be obtained.
(1) Intermediate pressure gas refrigerant introduced into the second chamber 31 b from each valve hole 41 a is guided to each supply passage 34 by the side surface portion 35 a of the bulging portion 35, and each injection port is passed through each supply passage 34. 30. For this reason, the flow of the refrigerant passing through the reed valve 42v toward the injection ports 30 can be made smooth. Further, by extending the bulging portion 35 toward the valve forming member 40, the bulging portion 35 is formed in the second chamber 31b as compared with the case where the bulging portion 35 is not extended toward the valve forming member 40. Dead volume can be reduced. That is, since the bulging portion 35 including the upper wall portion 35b to which the bolt 45 is fastened is used, the bulging portion is extended toward the valve forming member 40 only for the purpose of reducing the dead volume. There is no need. Therefore, the dead volume formed between the reed valve 42v and each injection port 30 can be reduced with a simple configuration.

  (2) The side surface portion 35a of the bulging portion 35 is curved in an arc shape. According to this, since the intermediate-pressure gas refrigerant introduced into the second chamber 31b from each valve hole 41a can easily flow along the side surface portion 35a of the bulging portion 35, it passes through the reed valve 42v. The flow of the gas refrigerant toward each injection port 30 can be further smoothed.

  (3) The bulging portion 35 is disposed at the center between the openings of the supply passages 34. According to this, compared with the case where the bulging portion 35 is disposed at a position close to either one of the supply passages 34, the second side from each valve hole 41 a is caused by the side surface portion 35 a of the bulging portion 35. The intermediate-pressure gas refrigerant introduced into the chamber 31 b can be made to flow evenly through the supply passages 34.

  (4) By only accommodating the valve forming member 40 in the accommodating recess 31, it is possible to prevent a reverse flow from the compression chamber 22 to the injection pipe 32 side through the refrigerant through each injection port 30. Therefore, the number of parts can be reduced and the scroll compressor 10 can be downsized as compared with the case where the valve forming member 40 is provided in each injection port 30.

  (5) The leading end portion of each reed valve 42v is disposed near the center connecting the supply passages 34 with a straight line L1. According to this, for example, each reed valve 42v is opened compared with the case where the tip portion of each reed valve 42v is disposed at a position close to either one of the supply passages 34, so that the valve hole The intermediate-pressure gas refrigerant introduced into the second chamber 31b from 41a can easily flow into the supply passages 34 and the injection ports 30 evenly.

  (6) Each reed valve 42v is, for example, a spool valve that reciprocates between a valve opening position and a valve closing position based on the relationship between the biasing force of the coil spring and the pressure of the intermediate-pressure gas refrigerant from the injection piping side. Responsiveness is better than. Therefore, the performance of the scroll compressor 10 at the time of a high load operation such as a heating operation is good.

In addition, you may change the said embodiment as follows.
As shown in FIG. 7, even if one valve hole 41 a (indicated by a two-dot chain line in FIG. 7) is formed in the valve plate 41 and one reed valve 42 v is formed in the reed valve forming plate 42. Good. In this case, it is preferable that the bulging portion 35 is disposed in a portion facing the center of the tip portion of the reed valve 42v in the second chamber 31b.

  In the embodiment, the bulging portion 35 may be disposed at a position close to either one of the supply passages 34. According to this, the flow rate of the gas refrigerant flowing toward each supply passage 34 can be adjusted by adjusting the arrangement position of the bulging portion 35.

In embodiment, the side part 35a of the bulging part 35 may be formed in the triangle shape, for example, and the shape of the side part 35a of the bulging part 35 is not specifically limited.
In the embodiment, the tip of each reed valve 42v may be disposed at a position close to either one of the supply passages 34.

  In the embodiment, the shape of each reed valve 42v is not particularly limited. In short, the tip of the reed valve 42v only needs to be formed in a shape that can cover the valve hole 41a.

  In the embodiment, for example, the valve hole 41a may be elliptical, and the shape of the valve hole 41a is not particularly limited. In this case, it is necessary to change the tip of the reed valve 42v to a shape that can cover the valve hole 41a.

  In the embodiment, three or more injection ports 30 may be formed on the fixed substrate 20a. In this case, three or more supply passages 34 are also formed in the bottom wall of the housing recess 31. A bulging portion 35 is disposed between the openings of the adjacent supply passages 34.

  In the embodiment, the retainer forming plate 43, the reed valve forming plate 42, and the valve plate 41 may be fastened by a plurality of bolts 45. For example, the number of bolts 45 may be four or more. Even in this case, each bolt 45 is preferably disposed so as to surround each reed valve 42v.

  In the embodiment, a plurality of press-fit pins as fastening portions are provided on the end face of the valve plate 41, and the press-fit pins are press-fitted into the bottom wall of the housing recess 31 and the upper wall portion 35b of the bulging portion 35. Thus, the retainer forming plate 43, the reed valve forming plate 42 and the valve plate 41 may be fastened to the bottom wall of the housing recess 31.

  In the embodiment, the shape of each injection port 30 and each supply passage 34 may be, for example, an elliptical shape along the spiral shape of the fixed spiral wall 20b, and the shape of each injection port 30 and each supply passage 34 is It is not particularly limited.

(Circle) in embodiment, the scroll compressor 10 may not be used for a vehicle air conditioner, and may be used for another air conditioner.
In the embodiment, the electric compressor is not limited to the scroll type, and may be, for example, a vane type or a roots type electric compressor.

Next, the technical idea that can be grasped from the above embodiment and other examples will be described below.
(A) Two valve holes and two reed valves are formed in the valve forming member, and the bulging portion is disposed at a portion facing between the tip portions of the reed valves.

(B) The valve forming member is formed with the valve hole and the reed valve one by one, and the bulging portion is disposed at a portion facing the center of the tip of the reed valve.
(C) The suction housing has two injection ports formed therein, and the intermediate pressure housing has two supply passages communicating with the two injection ports, respectively. The valve hole is disposed between the two supply passages.

  DESCRIPTION OF SYMBOLS 10 ... Scroll type compressor, 12 ... Suction housing structure which comprises suction housing, 13 ... Intermediate pressure housing, 14 ... Discharge housing, 15 ... Compression mechanism, 16 ... Electric motor, 20a ... Fixed board | substrate which comprises suction housing, DESCRIPTION OF SYMBOLS 22 ... Compression chamber, 25 ... Discharge chamber, 30 ... Injection port, 31 ... Storage recessed part, 33 ... Introduction port, 34 ... Supply passage, 35 ... Swelling part, 35a ... Side part functioning as a guide wall, 35b ... Upper wall 40, a valve forming member, 41a, a valve hole, 42v, a reed valve, 45, a bolt as a fastening portion, 50, an external refrigerant circuit.

Claims (3)

A discharge housing having an electric motor and a suction housing having a compression mechanism for compressing refrigerant sucked by rotation of the electric motor, and a discharge chamber for discharging refrigerant compressed in a compression chamber formed in the compression mechanism. A housing having an intermediate pressure that is higher than the suction pressure of the sucked refrigerant and lower than the discharge pressure of the discharged refrigerant. An electric compressor provided with a plurality of injection ports to be introduced into
An introduction port for introducing the intermediate pressure refrigerant from the external refrigerant circuit;
An accommodating recess communicating with the introduction port;
An intermediate pressure housing having a plurality of supply passages communicating the receiving recess and the injection port;
The intermediate pressure housing is disposed between the suction housing and the discharge housing;
A valve forming member having a valve hole and a reed valve for opening and closing the valve hole is housed in the housing recess,
The valve forming member is fastened to the intermediate pressure housing by a plurality of fastening portions,
At the bottom of the accommodating recess, openings of the plurality of supply passages are formed at positions shifted from the valve holes,
A bulging portion extending toward the valve forming member is formed between the openings of the adjacent supply passages,
The bulging portion includes guide walls for guiding the intermediate-pressure refrigerant introduced from the valve hole to the opening of the supply passage, respectively, on the side surface, and is opposed to the valve forming member, and includes at least the fastening portion. An electric compressor comprising an upper wall portion to which one is fastened.   The electric compressor according to claim 1, wherein the guide wall is curved in an arc shape.   The electric compressor according to claim 1, wherein the guide wall is disposed at a center between openings of the adjacent supply passages.