WO2016088342A1

WO2016088342A1 - Compressor

Info

Publication number: WO2016088342A1
Application number: PCT/JP2015/005875
Authority: WO
Inventors: 豊広加納; 井上　孝; 江原　俊行; 雅至井ノ上; 神谷　治雄
Original assignee: 株式会社デンソー
Priority date: 2014-12-04
Filing date: 2015-11-26
Publication date: 2016-06-09
Also published as: DE112015005489T5; JP6460595B2; JP2016108991A

Abstract

A compressor is provided with a compression mechanism part (10) having a first compression chamber (Va) and a second compression chamber (Vb) for compressing fluid, a housing (30) for accommodating the compression mechanism part, and a passage-forming member (14) for forming a passage through which the fluid is channeled in the housing. The housing is provided with an intermediate pressure intake port (30b) for taking in from the exterior intermediate pressure fluid, which will be merged with fluid undergoing the compression process in the first compression chamber and the second compression chamber. The passage-forming member has a branching part (14c) where the flow of intermediate pressure fluid taken in through the intermediate pressure intake port branches, a first injection passage (14a) for guiding one path of intermediate pressure fluid branched in the branching part to the first compression chamber, a second injection passage (14b) for guiding the other path of intermediate pressure fluid branched in the branching part to the second compression chamber, and extending passages (14d, 14e, 14f) for causing at least one of the first injection passage and the second injection passage to extend in a direction away from the branching part.

Description

Compressor

Cross-reference of related applications

This application is based on Japanese Patent Application No. 2014-245621 filed on December 4, 2014, the contents of which are incorporated herein by reference.

The present disclosure relates to a compressor that joins an intermediate pressure fluid sucked from the outside to a fluid in a compression process in a compression chamber.

Patent Document 1 discloses a compressor that joins an intermediate pressure fluid sucked from outside to a fluid in a compression process in a compression chamber.

In this type of compressor, an intermediate pressure suction port for sucking an intermediate pressure fluid from the outside and the compression chamber are intermittently connected. Therefore, pressure pulsation tends to occur in the intermediate pressure fluid in the injection passage, which is a fluid passage connecting the intermediate pressure suction port and the compression chamber. Further, such pressure pulsation causes an increase in noise and vibration of the entire compressor.

On the other hand, in the compressor of patent document 1, the enlarged diameter part which expanded the passage diameter rather than the other site | part was provided in the inside of an injection passage, and the intermediate pressure fluid of a liquid phase state is stored in this enlarged diameter part. . Then, the space in the enlarged diameter portion is made to function as a muffler space that attenuates the pressure pulsation of the fluid, and an increase in noise and vibration of the compressor is suppressed.

Japanese Patent Laid-Open No. 5-157069

However, in the compressor of Patent Document 1, it is difficult to ensure a sufficient volume of the space (muffler space) in the enlarged diameter portion because the enlarged diameter portion is only provided in the middle of the injection passage. For this reason, in the compressor of patent document 1, there is a possibility that the pressure pulsation of the fluid cannot be sufficiently attenuated in the space in the enlarged diameter portion, and the increase in noise and vibration of the compressor cannot be sufficiently suppressed. is there.

This indication aims at providing the compressor which can fully control the increase in noise and vibration in view of the above-mentioned point.

In one aspect of the present disclosure, the compressor forms a compression mechanism portion having a first compression chamber and a second compression chamber for compressing a fluid, a housing for accommodating the compression mechanism portion, and a passage through which the fluid flows in the housing. And a passage forming member. The housing is provided with an intermediate pressure suction port for sucking in from the outside an intermediate pressure fluid that is merged with a fluid in the compression process in the first compression chamber and the second compression chamber. The passage forming member includes a branch portion that branches the flow of the intermediate pressure fluid sucked from the intermediate pressure suction port, and a first injection passage that guides one of the intermediate pressure fluids branched at the branch portion to the first compression chamber side. A second injection passage for guiding the other intermediate pressure fluid branched at the branch portion to the second compression chamber side, and an extension passage for extending at least one of the first injection passage and the second injection passage to the side away from the branch portion And have.

According to this, the internal space of the extension passage can be made to function as a muffler space that attenuates the pressure pulsation of at least one fluid in the first injection passage and the second injection passage.

Furthermore, since the extension passage is formed so as to extend at least one of the first injection passage and the second injection passage to the side away from the branch portion, the internal volume (passage volume) of the extension passage can be easily expanded. Can do.

Therefore, it is easy to secure a volume that can sufficiently attenuate the pressure pulsation of the intermediate pressure fluid as the passage volume of the extension passage. As a result, increase in noise and vibration of the compressor in which the injection passage is formed can be sufficiently suppressed.

The extension passage may be formed in a shape that allows the first injection passage and the second injection passage to communicate with each other. The extension passage may be constituted by a first extension passage that extends the first injection passage and a second extension passage that extends the second injection passage.

In one aspect of the present disclosure, a compressor includes a compression mechanism section that forms a first compression chamber and a second compression chamber that compress a fluid, a housing that houses the compression mechanism section, and a passage that allows fluid to flow through the housing. A passage forming member to be formed. The housing is provided with an intermediate pressure suction port for sucking in from the outside an intermediate pressure fluid that is merged with a fluid in the compression process in the first compression chamber and the second compression chamber. The passage forming member includes a branch portion that branches the flow of the intermediate pressure fluid sucked from the intermediate pressure suction port, and a first injection passage that guides one of the intermediate pressure fluids branched at the branch portion to the first compression chamber side. And a second injection passage for guiding the other intermediate pressure fluid branched at the branching portion to the second compression chamber side. The passage shape of the first injection passage and the passage shape of the second injection passage are different from each other.

According to this, since the passage shape of the first injection passage and the passage shape of the second injection passage are different, the passage volume of the first injection passage and the passage volume of the second injection passage can be set to different values.

Therefore, pressure pulsations of fluids having different frequencies can be attenuated in the first injection passage and the second injection passage. As a result, increase in noise and vibration of the compressor in which the injection passage is formed can be sufficiently suppressed.

Here, the different passage shapes mean that the lengths of the passages are different and the cross-sectional areas of the passages are different.

Further, the passage forming member may form an extension passage that extends at least one of the first injection passage and the second injection passage to the side away from the branch portion.

The above and other objects, features, and advantages of the present disclosure will become more apparent from the following detailed description with reference to the accompanying drawings.
It is a whole block diagram of the heat pump cycle of 1st Embodiment. It is an axial sectional view of the compressor of a 1st embodiment. FIG. 3 is a cross-sectional view taken along line III-III in FIG. 2. It is sectional drawing corresponding to FIG. 3 of the channel | path formation plate of 2nd Embodiment. It is sectional drawing corresponding to FIG. 3 of the channel | path formation plate of the modification of 2nd Embodiment. It is sectional drawing corresponding to FIG. 3 of the channel | path formation plate of 3rd Embodiment. It is sectional drawing corresponding to FIG. 3 of the channel | path formation plate of 4th Embodiment. It is sectional drawing corresponding to FIG. 3 of the channel | path formation plate of 5th Embodiment. It is sectional drawing corresponding to FIG. 3 of the channel | path formation plate of the modification of 5th Embodiment. It is sectional drawing corresponding to FIG. 3 of the channel | path formation plate of another modification of 5th Embodiment. It is sectional drawing corresponding to FIG. 3 of the channel | path formation plate of 6th Embodiment. It is explanatory drawing of the gasket applied to the channel | path formation plate of 6th Embodiment.

(First embodiment)
The first embodiment will be described with reference to FIGS. In this embodiment, the compressor 1 is applied to a heat pump cycle (vapor compression refrigeration cycle) 100 that heats hot water using a heat pump type hot water heater. Therefore, the fluid compressed by the compressor 1 of this embodiment is a refrigerant of a heat pump cycle.

The heat pump cycle 100 is configured as a gas injection cycle (economizer-type refrigeration cycle) in which an intermediate-pressure gas-phase refrigerant of a cycle is merged with a refrigerant in a pressurizing process in the compression chamber of the compressor 1. More specifically, the heat pump cycle 100 of the present embodiment includes a compressor 1, a water-refrigerant heat exchanger 2, a first expansion valve 3, a gas-liquid separator 4, a second expansion valve, as shown in FIG. 5. It has the outdoor heat exchanger 6 grade | etc.,.

The water-refrigerant heat exchanger 2 is a heating heat exchanger that heats hot water by exchanging heat between the refrigerant discharged from the discharge port 40a of the compressor 1 and the hot water. The first expansion valve 3 is high-stage decompression means for decompressing the high-pressure refrigerant flowing out of the water-refrigerant heat exchanger 2 until it becomes intermediate-pressure refrigerant, and operates according to a control signal output from a control device (not shown). Is an electric expansion valve controlled.

The gas-liquid separator 4 is a gas-liquid separating means for separating the gas-liquid of the intermediate pressure refrigerant decompressed by the first expansion valve 3. The second expansion valve 5 is a low-stage decompression unit that decompresses the intermediate-pressure liquid-phase refrigerant flowing out from the liquid-phase refrigerant outlet of the gas-liquid separator 4 until it becomes a low-pressure refrigerant. The same as the expansion valve 3. The outdoor heat exchanger 6 is a heat absorption heat exchanger that evaporates the low-pressure refrigerant decompressed by the second expansion valve 5 by exchanging heat with the outside air.

A suction port 30 a of the compressor 1 is connected to the refrigerant outlet side of the outdoor heat exchanger 6, and an intermediate pressure suction port 30 b of the compressor 1 is connected to the gas-phase refrigerant outlet of the gas-liquid separator 4. Yes. Therefore, in this embodiment, the intermediate-pressure gas-phase refrigerant separated by the gas-liquid separator 4 is injected into the refrigerant in the pressurizing process in the compression chamber of the compressor 1.

In the heat pump cycle 100 of the present embodiment, carbon dioxide is used as the refrigerant, and the supercritical pressure in which the pressure of the high-pressure side refrigerant in the cycle from the discharge port of the compressor 1 to the inlet side of the first expansion valve 3 is equal to or higher than the critical pressure. It constitutes the refrigeration cycle. Furthermore, the refrigerant is mixed with oil (refrigeration oil) that lubricates each sliding portion inside the compressor 1, and a part of this oil circulates in the cycle together with the refrigerant.

In addition to the heat pump cycle 100, the heat pump hot water heater is a hot water storage tank that stores hot water heated by the water-refrigerant heat exchanger 2, and hot water supply between the hot water storage tank and the water-refrigerant heat exchanger 2. There are provided a hot water circulation circuit that circulates, a water pump that is arranged in the hot water circulation circuit and pumps hot water (none of which is shown).

Next, the detailed configuration of the compressor 1 will be described with reference to FIGS. In addition, the up and down arrows in FIG. 2 indicate the up and down directions in a state where the compressor 1 is mounted on the heat pump type hot water heater. The compressor 1 of the present embodiment is a so-called scroll type compressor, and includes a compression mechanism section 10, an electric motor section (electric motor section) 20, a housing 30, an oil separator 40, and the like.

The compression mechanism unit 10 sucks, compresses and discharges a refrigerant that is a compression target fluid. The electric motor unit 20 outputs a rotational driving force that drives the compression mechanism unit 10. The housing 30 forms an outer shell of the compressor 1 and houses the compression mechanism portion 10 and the electric motor portion 20 and the like therein. The oil separator 40 is disposed outside the housing 30 and separates oil from the high-pressure refrigerant compressed by the compression mechanism unit 10.

As shown in FIG. 2, the compressor 1 of the present embodiment has a shaft (rotating shaft) 25 that transmits a rotational driving force from the electric motor unit 20 to the compression mechanism unit 10 extending in the vertical direction (up and down direction). The part 10 and the motor part 20 are configured in a so-called vertical type in which the parts are arranged in the vertical direction. More specifically, in the compressor 1, the compression mechanism unit 10 is disposed on the lower side of the electric motor unit 20.

The housing 30 includes a cylindrical member 31 whose central axis extends in the vertical direction, a bowl-shaped upper lid member 32 that blocks the upper end portion of the cylindrical member 31, and a bowl-shaped lower lid member 33 that blocks the lower end portion of the cylindrical member 31. These are integrally joined to form a sealed container structure. The cylindrical member 31, the upper lid member 32, and the lower lid member 33 are all made of iron or an iron-based metal, and these members are joined by welding.

The housing 30 is formed with a suction port 30a, an intermediate pressure suction port 30b, and a high-pressure refrigerant outlet not shown.

The suction port 30a is a refrigerant suction port through which the low-pressure refrigerant flowing out of the outdoor heat exchanger 6 is sucked into the compression mechanism unit 10. The intermediate pressure suction port 30b is used to compress the intermediate pressure gas-phase refrigerant flowing out from the gas-phase refrigerant outlet of the gas-liquid separator 4 into the compression chambers of the compression mechanism unit 10 (in this embodiment, the first and second compression chambers shown in FIG. 2). Va, Vb) are intermediate pressure refrigerant inlets for merging with the refrigerant in the compression process. The high-pressure refrigerant outlet is a refrigerant outlet for allowing the high-pressure refrigerant discharged from the compression mechanism unit 10 to flow out to the oil separator 40 side disposed outside the housing 30.

The electric motor unit 20 includes a coil stator 21 that forms a stator and a rotor 22 that forms a rotor. A shaft 25 is fixed to the shaft center hole of the rotor 22 by press-fitting. Therefore, when electric power is supplied from the control device to the coils of the coil stator 21 and a rotating magnetic field is generated, the rotor 22 and the shaft 25 rotate together.

The shaft 25 is formed in a substantially cylindrical shape, and both end portions thereof are rotatably supported by a first bearing portion 26 and a second bearing portion 27 that are configured by sliding bearings, respectively. Further, an oil supply passage 25 a for supplying oil to the sliding portion between the outer surface of the shaft 25 and the first and

second bearing portions

26 and 27 is formed inside the shaft 25.

The first bearing portion 26 is formed in a middle housing 28 fixed so as to partition the space in the housing 30 into a space in which the electric motor portion 20 is disposed and a space in which the compression mechanism portion 10 is disposed. The lower end side (compression mechanism unit 10 side) is rotatably supported. The 2nd bearing part 27 is being fixed to the cylindrical member 31 of the housing 30 via the interposition member, and is supporting the upper end side (opposite side of the compression mechanism part 10) of the shaft 25 rotatably.

The compression mechanism unit 10 is a scroll type compression mechanism unit configured by a movable scroll 11 and a fixed scroll 12 each having a spiral tooth portion.

The movable scroll 11 has a disk-shaped movable side substrate part 111 and a spiral movable side tooth part 112 protruding from the movable side substrate part 111 toward the fixed scroll 12 side. The fixed scroll 12 has a disk-shaped fixed side substrate portion 121 and a spiral fixed side tooth portion 122 protruding from the fixed side substrate portion 121 toward the movable scroll 11 side.

Furthermore, the fixed scroll 12 is fixed to the lower side of the middle housing 28 by press-fitting the outer peripheral side surface of the fixed-side substrate portion 121 into the inner peripheral side surface of the cylindrical member 31 of the housing 30. The movable scroll 11 is disposed in a space formed between the middle housing 28 and the fixed scroll 12.

The movable scroll 11 and the fixed scroll 12 are arranged so that the plate surfaces of the

respective substrate portions

111 and 121 face each other, and the

respective tooth portions

112 and 122 are engaged with each other, so that the tooth portion of one scroll is engaged. The tip portion is disposed so as to contact the substrate portion of the other scroll.

Thereby, each tooth part 112,122 contacts in several places, and when it sees from the axial direction of the central axis of the shaft 25 between each tooth part 112,122, it forms in a crescent moon shape. A plurality of compression chambers are formed.

FIG. 2 schematically shows the first compression chamber Va and the second compression chamber Vb into which the intermediate pressure refrigerant that has flowed in via the intermediate pressure suction port 30b is injected for the sake of clarity. The first compression chamber Va and the second compression chamber Vb are formed at positions that are symmetric with respect to the central axis of the shaft 25. Further, the refrigerant pressure in the first compression chamber Va is equal to the refrigerant pressure in the second compression chamber Vb.

A cylindrical boss portion 113 into which the lower end portion of the shaft 25 (end portion on the compression mechanism portion 10 side) is inserted is formed at the center portion on the upper surface side of the movable side substrate portion 111 of the movable scroll 11. . On the other hand, the lower end portion of the shaft 25 is an eccentric portion 25 b that is eccentric with respect to the rotation center of the shaft 25. Accordingly, the eccentric portion 25 b of the shaft 25 is inserted into the boss portion 113 of the movable side substrate portion 111 of the movable scroll 11.

Furthermore, between the movable scroll 11 and the middle housing 28, a rotation prevention mechanism (not shown) for preventing the movable scroll 11 from rotating around the eccentric portion 25b is provided. For this reason, when the shaft 25 rotates, the movable scroll 11 turns (revolves) with the rotation center of the shaft 25 as the revolution center without rotating around the eccentric portion 25b.

And by this revolving motion, the compression chamber described above is displaced from the outer peripheral side to the center side around the shaft 25 while reducing the volume. Furthermore, in this embodiment, the confidentiality of the compression chamber is improved by disposing a tip seal at the tip of the

tooth portions

112 and 122 of the respective scrolls. As such a chip seal, one formed of PEEK (polyether ether ketone) resin can be employed.

The suction port 30a formed in the housing 30 is positioned on the outermost peripheral side of the compression chamber via the suction passage formed in the fixed scroll 12 and has the largest volume on the suction side. Communicating with Therefore, the fixed scroll 12 of the present embodiment also has a function as a passage forming member that forms a passage through which the refrigerant flows in the housing 30.

The intermediate pressure suction port 30b is an intermediate position in the process of being displaced from the outermost peripheral side to the center side in the compression chamber via the first and

second injection passages

14a and 14b formed in the fixed scroll 12 and the passage forming plate 14. Are communicated with the first compression chamber Va and the second compression chamber Vb. Therefore, the passage forming plate 14 of this embodiment constitutes a passage forming member together with the fixed scroll 12.

The passage forming plate 14 is formed of a disk-shaped metal member, and is fixed to the lower surface of the fixed scroll 12 by fixing means such as bolting. Further, as shown in FIG. 3, the passage forming plate 14 is recessed on the surface on the fixed scroll 12 side so that the branching portion 14c, the first injection passage 14a, the second injection passage 14b, and the extension passage 14d are formed. Is formed.

The positional relationship among the first injection passage 14a, the second injection passage 14b, the branching portion 14c, the suction port 30a, the intermediate pressure suction port 30b, and the like is as shown in FIG. That is, in FIG. 2, the first injection passage 14a, the second injection passage 14b, the branching portion 14c, the suction port 30a, the intermediate pressure suction port 30b, and the like are schematically illustrated on one cross-sectional view for the sake of clarity of explanation. It is shown.

The branch part 14c is a part that branches the flow of the intermediate pressure refrigerant sucked from the intermediate pressure suction port 30b. The first injection passage 14a is a refrigerant passage that guides one intermediate-pressure refrigerant branched by the branch portion 14c to the first compression chamber Va side. The second injection passage 14b is a refrigerant passage that guides the other intermediate-pressure refrigerant branched by the branch portion 14c to the second compression chamber Vb side.

The extension passage 14d is a refrigerant passage that extends the first injection passage 14a and the second injection passage 14b to the side away from the branch portion 14c. Furthermore, the extension passage 14d of the present embodiment is formed in a semicircular arc shape so as to connect the first injection passage 14a and the second injection passage 14b when viewed from the central axis direction of the shaft 25.

For this reason, the first injection passage 14a, the second injection passage 14b, and the extension passage 14d of the present embodiment are annularly connected when viewed from the axial direction of the central axis of the shaft 25 as shown in FIG. The In the present embodiment, the first injection passage 14a, the second injection passage 14b, and the extension passage 14d in the passage formation plate 14 have constant depth dimensions (the amount of recesses in the front and back directions).

Further, inside the fixed scroll 12, the intermediate pressure refrigerant sucked from the intermediate pressure suction port 30b is allowed to flow only from the first injection passage 14a side (branch portion 14c side) to the first compression chamber Va side. 1 check valve 51 is arranged. Further, a second check valve 52 that allows only the intermediate pressure refrigerant to flow from the second injection passage 14 b side (branch portion 14 c side) to the second compression chamber Vb side is disposed inside the fixed scroll 12. Yes.

The first and

second check valves

51 and 52 are constituted by a reed valve formed of a plate-like member and a seat member formed with a passage for opening and closing the reed valve. Since such a reed valve type check valve can be accommodated in a relatively small accommodation space, the internal volume (dead volume) of the refrigerant passage downstream from the first and

second check valves

51 and 52. It is effective in that it does not unnecessarily expand.

Further, a discharge hole 123 through which the refrigerant compressed in the compression chamber is discharged is formed at the center of the fixed side substrate 121 of the fixed scroll 12. Further, a discharge chamber 124 communicating with the discharge hole 123 is formed below the discharge hole 123. The discharge chamber 124 is provided with a discharge valve (reed valve) that prevents the refrigerant from flowing backward from the discharge chamber 124 side to the compression chamber Vc side, and a stopper 16 that regulates the maximum opening of the discharge valve.

Inside the housing 30, a refrigerant passage (not shown) that leads from the discharge chamber 124 to the refrigerant outlet formed in the housing 30 is formed. Further, a refrigerant inlet 40b of the oil separator 40 is connected to the refrigerant outlet. The oil separator 40 includes a cylindrical member 41 extending in the vertical direction, and the refrigerant pressurized by the compression mechanism unit 10 is swirled in a space formed therein, and the gas phase refrigerant and the oil are subjected to centrifugal force. And isolate.

The high-pressure gas-phase refrigerant separated by the oil separator 40 is discharged from the discharge port 40a formed on the upper side of the oil separator 40 to the water-refrigerant heat exchanger 2 side. On the other hand, the oil separated by the oil separator 40 is stored in a lower portion of the oil separator 40, and the first and first compression mechanisms 10 and the shaft 25 in the housing 30 are connected to the first and first members via an oil passage (not shown). 2 Supplied to a sliding portion with the bearing

portions

26 and 27.

Next, the operation of the compressor 1 of the present embodiment having the above configuration will be described. When electric power is supplied to the electric motor unit 20 of the compressor 1 and the rotor 22 and the shaft 25 rotate, the movable scroll 11 turns (revolves) with respect to the shaft 25. As a result, the crescent-shaped compression chamber formed between the movable side tooth portion 112 of the movable scroll 11 and the fixed side tooth portion 122 of the fixed scroll 12 moves while turning around the shaft 25 from the outer peripheral side to the center side. To go.

At this time, the low-pressure refrigerant flowing out of the outdoor heat exchanger 6 is sucked into the suction-side compression chamber positioned on the outermost peripheral side and communicating with the suction port 30a through the suction port 30a. As the shaft 25 rotates, the compression chamber into which the low-pressure refrigerant has flowed moves to an intermediate position communicating with the downstream refrigerant passage 51 while reducing its volume.

In a state where the compression chamber moves to the intermediate position and the pressure P2 of the intermediate pressure gas phase refrigerant on the intermediate pressure suction port 30b side is higher than the refrigerant pressure P1 on the first and second compression chambers Va and Vb side, The first and

second check valves

51 and 52 are opened by the pressure difference between the refrigerant pressure P1 on the second compression chambers Va and Vb side and the refrigerant pressure P2 on the intermediate pressure suction port 30b side. Thereby, the intermediate-pressure gas-phase refrigerant separated by the gas-liquid separator 4 and sucked from the intermediate-pressure suction port 30b is injected into the first and second compression chambers Va and Vb.

Furthermore, when the volume of the compression chamber is reduced with the rotation of the shaft 25 and the refrigerant pressure P1 on the first and second compression chambers Va, Vb side exceeds the refrigerant pressure P2 on the intermediate pressure suction port 30b side, The first and

second check valves

51 and 52 are closed by the pressure difference between the refrigerant pressure P1 on the second compression chambers Va and Vb side and the refrigerant pressure P2 on the intermediate pressure suction port 30b side. This prevents the refrigerant from flowing backward from the compression chamber Vc side to the intermediate pressure suction port 30b side.

Further, as the shaft 25 rotates, the compression chamber moves to a position where it communicates with the discharge hole 123 of the fixed scroll 12 on the center side, and discharge occurs when the pressure of the high-pressure refrigerant in the working chamber Vc exceeds the valve opening pressure of the discharge valve. The valve opens. As a result, the high-pressure refrigerant is discharged into the discharge chamber 124. The high-pressure refrigerant discharged to the discharge chamber 124 is separated from the oil by the oil separator 40 and discharged from the discharge port 40a to the water-refrigerant heat exchanger 2 side.

As described above, in the compressor 1 of the present embodiment, the heat pump cycle 100 can suck the refrigerant, compress it, and discharge it.

Here, in the compressor in which the intermediate pressure fluid sucked from the outside is joined to the fluid in the compression process in the compression chamber like the compressor 1 of the present embodiment, the intermediate pressure suction port and the compression chamber are intermittently provided. Because of the connection, pressure pulsation is likely to occur in the intermediate pressure refrigerant in the injection passage (first and

second injection passages

14a and 14b in this embodiment). Further, such pressure pulsation causes an increase in noise and vibration of the entire compressor.

In contrast, since the extension passage 14d is formed in the compressor 1 of the present embodiment, the pressure of the intermediate pressure refrigerant in the first and

second injection passages

14a and 14b is formed in the internal space of the extension passage 14d. It can function as a muffler space that attenuates pulsation.

Further, the extension passage 14d is formed so as to extend the first injection passage 14a and the second injection passage 14b to the side away from the branch portion 14c. According to this, it is possible to easily expand the internal volume (passage volume) of the extension passage 14d by effectively utilizing the portion of the passage formation plate 14 where the first and

second injection passages

14a and 14b are not formed. .

Therefore, it is easy to secure a volume capable of sufficiently attenuating the pressure pulsation of the target frequency as the passage volume of the extension passage 14d. As a result, in the compressor 1 of this embodiment, increase in noise and vibration can be sufficiently suppressed even if the first and

second injection passages

14a and 14b are formed.

In the present embodiment, the extension passage 14d is formed so as to communicate the first injection passage 14a and the second injection passage 14b. Therefore, the passage volume of the extension passage 14d can be more easily expanded.

Further, by adjusting the passage length and the passage cross-sectional area of the extension passage 14d so that the pressure pulsation on the first injection passage 14a side and the pressure pulsation on the second injection passage 14b side cancel each other and attenuate, the effect is further improved. In particular, increase in noise and vibration of the compressor can be suppressed.

Further, in the configuration in which the

check valves

51 and 52 are arranged in the

injection passages

14a and 14b as in the compressor 1 of the present embodiment, the opening and closing operation of the

check valves

51 and 52 causes the inside of the

injection passages

14a and 14b. Pressure pulsation is likely to occur in the refrigerant. Therefore, it is extremely effective in the compressor in which the check valve is arranged in the injection passage to suppress the increase in noise and vibration as in the present embodiment.

(Second Embodiment)
In the present embodiment, as shown in FIG. 4, an example is described in which the extension passage is configured by a first extension passage 14e that extends the first injection passage 14a and a second extension passage 14f that extends the second injection passage 14b. To do. As is clear from FIG. 4, the first and

second extension passages

14 e and 14 f are both arcuately shaped when viewed from the central axis direction of the shaft 25, and the tip portions communicate with each other. Not done.

FIG. 4 is a drawing corresponding to FIG. 3 of the first embodiment, and the same reference numerals are given to the same or equivalent parts as in the first embodiment. The same applies to the following drawings.

Other configurations and operations are the same as those in the first embodiment. Accordingly, when the compressor 1 of the present embodiment is operated, the first and

second extension passages

14e and 14f are formed, so that the noise and vibration of the compressor 1 are sufficiently increased as in the first embodiment. Can be suppressed.

Furthermore, in the compressor 1 of the present embodiment, the first and

second extension passages

14e and 14f are in the form of a tip. For this reason, the first and second pulsating waves of the refrigerant in the first and

second injection passages

14a and 14b and the pulsating waves reflected at the tips of the first and

second extension passages

14e and 14f cancel each other. By adjusting the passage lengths and the like of the

extension passages

14e and 14f, the increase in noise and vibration of the compressor can be suppressed more effectively.

Further, according to the study by the present inventors, the passage lengths of the first and

second extension passages

14e and 14f are about 1 / 8λ or more and about 3 / 8λ or less with respect to the wavelength λ of the pulsating wave. By doing so, it has been confirmed that an increase in noise and vibration of the compressor can be effectively suppressed.

The length of the first extension passage 14e may be the length of the center line of the first extension passage 14e as shown by the broken line in FIG. More specifically, the length of the center line of the passage extending from the communication of the first check valve 51 to the first compression chamber Va to the tip of the branch portion 14c of the first extension passage 14e may be employed. . The same applies to the length of the second extension passage 14f.

Furthermore, in order to make the passage lengths of the first and

second extension passages

14e and 14f desired lengths, for example, as shown in the modified example of FIG. The extension passage 14e and the second extension passage 14f may be arranged so that at least a part thereof is superposed.

(Third embodiment)
In the present embodiment, as shown in FIG. 6, an example will be described in which the extended passage 14d described in the first embodiment is formed in a shape in which the passage cross-sectional area changes.

More specifically, the extension passage 14d of this embodiment reduces the passage cross-sectional area by gradually reducing the passage width dimension with distance from the first and

second injection passages

14a and 14b. . Other configurations and operations are the same as those in the first embodiment. Therefore, when the compressor 1 of this embodiment is operated, the same effect as that of the first embodiment can be obtained.

Furthermore, according to the compressor 1 of the present embodiment, the passage cross-sectional area gradually changes in the extension passage 14d as the distance from the first and

second injection passages

14a and 14b increases. The frequency of the pressure pulsation that can be attenuated can be gradually changed. Therefore, pressure pulsations in a wide frequency band can be attenuated, and increase in noise and vibration of the compressor 1 can be suppressed more effectively.

(Fourth embodiment)
In the present embodiment, as shown in FIG. 7, the passage length of the first extension passage 14e and the passage length of the second extension passage 14f described in the second embodiment are different from each other. Other configurations and operations are the same as those in the second embodiment. Therefore, when the compressor 1 of this embodiment is operated, the same effect as that of the second embodiment can be obtained.

Furthermore, according to the compressor 1 of the present embodiment, since the passage length of the first extension passage 14e and the passage length of the second extension passage 14f are different, the first and second extension passages 14e, The frequency of the pressure pulsation that can be attenuated at 14f can be set to different values. Therefore, the range of the pressure pulsation frequency band that can be attenuated can be expanded, and the increase in noise and vibration of the compressor 1 can be more effectively suppressed.

For example, the pressure pulsation generated when the compressor 1 of the present embodiment is applied to a system that rotates at two different rotational speeds and the passage length of the first extension passage 14e is rotated at one rotational speed is attenuated. It may be determined so that the pressure pulsation generated when the passage length of the second extension passage 14f is rotated at the other rotational speed is attenuated. According to this, it is possible to suppress an increase in noise and vibration of the compressor 1 when operated at any rotational speed.

(Fifth embodiment)
In the present embodiment, as shown in FIG. 8, an example will be described in which the passage shape of the first injection passage 14a and the passage shape of the second injection passage 14b are different from those of the second embodiment.

Specifically, in the compressor 1 according to the present embodiment, the passage length of the first injection passage 14a is changed by changing the positions of the intermediate pressure suction port 30b and the branching portion 14c with respect to the second embodiment. It is shorter than the passage length of the 2-injection passage 14b. Other configurations and operations are the same as those in the second embodiment. Therefore, when the compressor 1 of this embodiment is operated, the same effect as that of the second embodiment can be obtained.

Furthermore, according to the compressor 1 of the present embodiment, the passage shape of the first injection passage 14a and the passage shape of the second injection passage 14b are different, so the first injection passage 14a and the second injection passage 14b Different frequency pulsations can be attenuated.

More specifically, the internal spaces of the first and

second injection passages

14a and 14b each function as a muffler space. Therefore, if the passage shapes of the first and

second injection passages

14a and 14b are different, and the passage volumes of the first and

second injection passages

14a and 14b are different values, the first and

second injection passages

14a and 14b. Thus, pressure pulsations with different frequencies can be attenuated.

Further, the means for making the passage shape of the first injection passage 14a different from the passage shape of the second injection passage 14b is not limited to changing the length of each passage.

For example, as shown in the modification of FIG. 9, the passage width dimension of the first injection passage 14a may be larger than the passage width dimension of the second injection passage 14b. As shown in the modification of FIG. 10, the passage width dimension of the first injection passage 14a may be made smaller than the passage width dimension of the second injection passage 14b.

(Sixth embodiment)
In the present embodiment, as shown in FIG. 11, the passage shape of the first injection passage 14a and the passage shape of the second injection passage 14b are different from each other as in the fifth embodiment, and the first injection passage 14a and An example in which the second injection passage 14b is formed in a shape in which the passage sectional area changes will be described.

More specifically, the first injection passage 14a is formed in a shape in which the passage cross-sectional area gradually increases from the branch portion 14c. The second injection passage 14b is formed with a throttle portion 14g that reduces the cross-sectional area of the passage. In the present embodiment, the first extension passage 14e is eliminated. Other configurations and operations are the same as those of the fifth embodiment. Therefore, when the compressor 1 of this embodiment is operated, the same effect as that of the fifth embodiment can be obtained.

Here, as described in the fifth embodiment, the internal spaces of the first and

second injection passages

14a and 14b each function as a muffler space. For this reason, the pressure pulsation damping effect of the intermediate pressure refrigerant can be improved by increasing the passage volume of the first and

second injection passages

14a and 14b. On the other hand, if the passage volumes of the first and

second injection passages

14a and 14b are enlarged, the compressor 1 as a whole is likely to be enlarged.

Further, the pressure pulsation of the intermediate pressure refrigerant is achieved by forming the throttle portions 14g and the like in the first and

second injection passages

14a and 14b and reducing the flow rate of the refrigerant flowing through the first and

second injection passages

14a and 14b. Energy can be reduced. On the other hand, if the flow rate of the refrigerant flowing through the first and

second injection passages

14a and 14b is reduced, it becomes impossible to join the intermediate pressure refrigerant having an appropriate flow rate to the refrigerant in the compression process in the compression chamber.

In the gas injection cycle, if the intermediate pressure refrigerant having an appropriate flow rate cannot be merged with the refrigerant in the compression process in the compression chamber, the coefficient of performance (COP) of the cycle by configuring the gas injection cycle. It becomes difficult to obtain the improvement effect.

On the other hand, in the present embodiment, the first injection passage 14a and the second injection passage 14b are shaped so that the passage cross-sectional area changes to form the throttle portion 14g and the like. According to this, the passage volume of the first and

second injection passages

14a and 14b and the flow rate of the refrigerant flowing through the first and

second injection passages

14a and 14b are adjusted so that the pressure pulsation of the target frequency can be attenuated. Can do.

More specifically, the volume component C of the first and

second injection passages

14a and 14b can be adjusted by adjusting the passage volume of the first and

second injection passages

14a and 14b. The resistance component R of the first and

second injection passages

14a and 14b can be adjusted by adjusting the flow rate of the refrigerant flowing through the first and

second injection passages

14a and 14b.

Therefore, the shape of the first injection passage 14a and the second injection passage 14b can be adjusted so that the pressure pulsation of the target frequency can be attenuated, like a low-pass filter in an electric circuit. As a result, an increase in noise and vibration of the compressor 1 can be suppressed more effectively.

By the way, in this embodiment, in order to form the first and

second injection passages

14a and 14b, the passage forming plate 14 is fixed to the lower surface of the fixed scroll 12 by bolting. For this reason, in order to prevent refrigerant leakage from the gap between the lower surface of the fixed scroll 12 and the passage forming plate 14, a gasket 15 that is a flat seal member is provided in the gap between the fixed scroll 12 and the passage forming plate 14. It is arranged.

More specifically, in this embodiment, the gasket 15 is arranged in the range shown in the hatched area in FIG. Further, the gasket 15 is formed with first and

second ribs

15a and 15b protruding to at least one of the fixed scroll 12 side and the passage forming plate 14 side. The first and

second ribs

15a and 15b are crushed when the passage forming plate 14 is fixed to the fixed scroll 12, and fulfill the function of improving the sealing performance.

Further, in the gasket 15, as shown by a thick solid line in FIG. 12, an annular first rib 15a is formed around the discharge chamber 124, and the outer circumferences of the first and

second injection passages

14a and 14b and the second extension passage 14f are formed. A second rib 15b is formed on the side. That is, the first and

second ribs

15a and 15b are formed in a double annular shape when viewed from the direction in which the gasket 15 is crushed (in the present embodiment, the central axis direction of the shaft 25).

Further, the second rib 15b is shaped to be recessed on the inner peripheral side, and four inner peripheral side bolt holes 151 into which fastening bolts are inserted are arranged at substantially equal angular intervals (approximately 90 ° intervals) around the first rib 15a. The six outer peripheral bolt holes 152 are arranged around the second rib 15b at substantially equal angular intervals (approximately 60 ° intervals).

As described above, the first and

second ribs

15a and 15b are formed in an annular shape, and the inner peripheral side bolt hole 151 and the outer peripheral side bolt 152 hole are arranged in an annular shape, so that the passage forming plate 14 is positioned below the fixed scroll 12. When attached to the side surface, the first and

second ribs

15a and 15b of the gasket 15 can be uniformly crushed, and a good sealing property can be obtained. Furthermore, in order to obtain a good sealing property, it is desirable to provide ribs also around the inner peripheral side bolt hole 151 as shown by a thick solid line in FIG.

(Other embodiments)
The present disclosure is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present disclosure.

In each of the above embodiments, the example in which the extension passages 14d to 14f are formed in the passage formation plate 14 has been described. For example, as in the fifth and sixth embodiments, the shape of the first injection passage 14a and the second shape If the shape of the passage of the injection passage 14b is different, the extension passages 14d to 14f are not essential components. Furthermore, the first and

second extension passages

14e and 14f do not necessarily have to be formed at the same time. If the pressure pulsation at the target frequency can be attenuated as in the sixth embodiment, either one is formed. May be.

In each of the above-described embodiments, the example in which the passage width dimension of each of the passages 14a to 14f is changed in order to change the passage cross-sectional area of the first and

second injection passages

14a and 14b and the extension passages 14d to 14f has been described. However, the means for changing the passage cross-sectional area is not limited to this. For example, the passage cross-sectional area may be changed by changing the vertical dimension (the amount of depression) of each of the passages 14a to 14f in the passage forming plate 14.

Furthermore, the first and

second injection passages

14a and 14b and the extension passages 14d to 14f do not necessarily have to change all the passage cross-sectional areas. If the pressure pulsation of the target frequency can be attenuated, the passages 14a to 14f What is necessary is just to change at least 1 passage cross-sectional area of 14f.

In each of the above-described embodiments, an example in which a scroll-type compression mechanism unit is employed as the compression mechanism unit 10 has been described. However, the compression mechanism unit 10 is not limited thereto. That is, as the compression mechanism unit 10, any type of compression mechanism unit may be adopted as long as the first and second compression chambers Va and Vb that can join the intermediate pressure fluid to the fluid in the compression process are formed. May be.

For example, it has a cylinder that forms a columnar space having an elliptical cross section, a columnar rotor disposed inside the columnar space, and a plurality of vanes that protrude from the outer peripheral surface side of the rotor so as to contact the inner peripheral surface of the cylinder. The compression chamber may be a so-called inner vane type compression mechanism portion formed by a space partitioned by the inner peripheral surface of the cylinder, the outer peripheral surface of the rotor, and the vanes.

In the above embodiments, the example in which the compressor 1 is applied to the heat pump cycle 100 of the heat pump type hot water heater has been described, but the application of the compressor 1 is not limited to this. That is, the compressor 1 can be applied to a wide range of uses as a compressor that compresses various fluids.

Furthermore, the compressor 1
A radiator that exchanges heat between the high-pressure refrigerant discharged from the compressor and the fluid to be heated (or outside air);
A branching portion for branching the flow of the high-pressure refrigerant flowing out of the radiator;
A high-stage expansion valve that depressurizes one high-pressure refrigerant branched at the branching section until it becomes an intermediate-pressure refrigerant;
An internal heat exchanger for exchanging heat between the other high-pressure refrigerant branched at the branch portion and the intermediate-pressure refrigerant decompressed by the high-stage expansion valve;
A low-stage side expansion valve that depressurizes the high-pressure refrigerant flowing out of the internal heat exchanger until it becomes a low-pressure refrigerant;
An evaporator that evaporates the low-pressure refrigerant by exchanging heat between the low-pressure refrigerant flowing out from the low-stage expansion valve and the outside air (or the fluid to be cooled),
A gas injection cycle configured to suck intermediate pressure refrigerant flowing out of the internal heat exchanger into the intermediate pressure suction port 30b of the compressor 1 and suck low pressure refrigerant flowing out of the evaporator into the suction port 30a of the compressor 1. You may apply to.

In the above embodiment, the vertical type compressor 1 has been described. However, the shaft (rotating shaft) 25 extends in the horizontal direction, and the compression mechanism unit 10 and the motor unit 20 are arranged in the horizontal direction (lateral direction). You may be comprised as a horizontal installation type compressor.

In the above-described embodiment, an example in which a reed valve is employed as the first and

second check valves

51 and 52 has been described. However, the first and

second check valves

51 and 52 are not limited thereto. For example, a free valve (spool valve) that is displaced according to the differential pressure between the refrigerant pressure P1 on the compression chamber Vc side and the refrigerant pressure P2 on the intermediate pressure suction port 30b side may be employed.

Further, the means disclosed in each of the above embodiments may be appropriately combined within a practicable range. For example, the modification of the second embodiment may be applied to the first and

second extension passages

14e and 14f of the fourth embodiment. That is, when viewed from the radial direction of the shaft 25, the first and

second extension passages

14e and 14f having different lengths may be arranged so that at least a part thereof is superposed.

Claims

A compression mechanism (10) having a first compression chamber (Va) and a second compression chamber (Vb) for compressing fluid;
A housing (30) for accommodating the compression mechanism (10);
A passage forming member (14) that forms a passage through which fluid flows in the housing (30),
The housing (30) has an intermediate pressure suction port (30b) for sucking in from the outside an intermediate pressure fluid that joins the fluid in the compression process in the first compression chamber (Va) and the second compression chamber (Vb). Provided,
The passage forming member (14)
A branch portion (14c) for branching the flow of the intermediate pressure fluid sucked from the intermediate pressure suction port (30b);
A first injection passage (14a) for guiding one intermediate pressure fluid branched at the branch portion (14c) toward the first compression chamber (Va);
A second injection passage (14b) for guiding the other intermediate pressure fluid branched at the branch portion (14c) toward the second compression chamber (Vb);
The compressor having an extension passage (14d, 14e, 14f) for extending at least one of the first injection passage (14a) and the second injection passage (14b) to the side away from the branch portion (14c).
A compression mechanism (10) having a first compression chamber (Va) and a second compression chamber (Vb) for compressing fluid;
A housing (30) for accommodating the compression mechanism (10);
A passage forming member (14) that forms a passage through which fluid flows in the housing (30),
The housing (30) has an intermediate pressure suction port (30b) for sucking in from the outside an intermediate pressure fluid that joins the fluid in the compression process in the first compression chamber (Va) and the second compression chamber (Vb). Provided,
The passage forming member (14)
A branch portion (14c) for branching the flow of the intermediate pressure fluid sucked from the intermediate pressure suction port (30b);
A first injection passage (14a) for guiding one intermediate pressure fluid branched at the branch portion (14c) toward the first compression chamber (Va);
A second injection passage (14b) for guiding the other intermediate pressure fluid branched at the branch portion (14c) to the second compression chamber (Vb) side;
The compressor in which the passage shape of the first injection passage (14a) and the passage shape of the second injection passage (14b) are different.
The compressor according to claim 2, wherein at least one of the first injection passage (14a) and the second injection passage (14b) is formed in a shape in which a passage sectional area changes.
The passage forming member (14) is an extension passage (14d, 14e, 14f) that extends at least one of the first injection passage (14a) and the second injection passage (14b) away from the branch portion (14c). The compressor according to claim 2 or 3 which forms).
The compressor according to claim 1 or 4, wherein the extension passage (14d) is formed in a shape that allows the first injection passage (14a) and the second injection passage (14b) to communicate with each other.
The extension passage is constituted by a first extension passage (14e) for extending the first injection passage (14a) and a second extension passage (14f) for extending the second injection passage (14b). The compressor according to 1 or 4.
The compressor according to claim 6, wherein a passage length of the first extension passage (14e) and a passage length of the second extension passage (14f) are different from each other.
The said 1st extension channel | path (14e) and the said 2nd extension channel | path (14f) are mutually formed in circular arc shape, and when it sees from radial direction, at least one part has overlapped and is arrange | positioned. Or the compressor according to 7;
The compressor according to any one of claims 1, 4 to 8, wherein the extension passages (14d, 14e, 14f) are formed in a shape in which a passage cross-sectional area changes.
A first check valve (51) that only allows fluid to flow from the intermediate pressure suction port (30b) side to the first compression chamber (Va) side;
10. A second check valve (52) that allows only fluid to flow from the intermediate pressure suction port (30 b) side to the second compression chamber (Vb) side. The compressor described in 1.