JP7329772B2 - Compressor with injection mechanism - Google Patents

Description

TECHNICAL FIELD The present invention relates to a compressor with an injection mechanism for use in an injection cycle.

Patent Literature 1 shows a scroll-type compressor with an injection mechanism used in a conventional injection cycle. In order to improve the efficiency of this compressor with an injection mechanism, the discharge reed valve is fixed at an angle to the end plate of the fixed scroll. By fixing the injection valve that can open and close the injection port, the dead volume of the discharge port is reduced while providing a space for the injection port. In other words, under the constraint that the end plate of the fixed scroll should be thick, an injection port was provided to improve efficiency.

Japanese Patent No. 5842637

The present disclosure provides a compressor with an injection mechanism in which an injection port can be installed without being subject to restrictions such as increasing the thickness of the compression mechanism when configuring the injection port.

A compressor with an injection mechanism of the present disclosure has a compression mechanism section that sucks a low-pressure working fluid into a sealed container and compresses it to a high-pressure state, and the compression mechanism section has an outlet from a compression chamber to a discharge chamber. In the compressor provided with a discharge valve for preventing backflow, the compression mechanism part draws the working fluid in an intermediate pressure state between low pressure and high pressure from the outside of the sealed container into the compression chamber via the injection pipe. and a check valve for suppressing reverse flow of the working fluid from the compression chamber to the intermediate pressure path . a valve seat of the check valve is provided on the partition member; and a reed valve type valve body is used for the discharge valve and the check valve, and at least one of each is used. The valve body of is constructed on an integral seat .

In the present disclosure, since the movable range of the discharge valve is regulated by the partition member that partitions and forms the intermediate pressure path for injection, the vicinity of the discharge port that opens and closes the discharge valve without being subject to restrictions such as increasing the thickness of the compression mechanism. An injection port can be installed at a position, and a high-capacity and high-efficiency compressor with an injection mechanism can be provided.

FIG. 1 is a vertical cross-sectional view of a scroll compressor according to this embodiment. FIG. 1 is an enlarged cross-sectional view of a main part of the compression mechanism shown in FIG. CC arrow line view of FIG. Open state diagram of the communication passage with the back pressure chamber and the injection port associated with the orbital motion of the scroll compressor Explanatory drawing showing the positional relationship between the communication passage with the back pressure chamber and the seal member accompanying the orbital motion of the scroll compressor. Refrigerating cycle diagram according to one embodiment of the present invention AA line view of FIG. 2 BB line arrow view of FIG. Intermediate pressure path and discharge port sectional view according to Embodiment 2

(Knowledge, etc. on which this disclosure is based)
At the time when the inventors came up with the present disclosure, there was a scroll compressor with an injection mechanism described in Patent Document 1. In this compressor with an injection mechanism, since the valve chamber containing the injection valve is provided in the end plate of the fixed scroll, the size of the injection valve is required as the thickness of the end plate, which increases the thickness of the end plate compared to the case without the injection mechanism. There is a problem that the effect of the dead volume of the discharge port associated with this is increased, and the efficiency improvement effect cannot be sufficiently obtained. In particular, when the injection port is arranged at a position relatively close to the discharge reed valve, the effect of obliquely arranging the discharge reed valve is reduced, and the dead volume reduction effect is also limited. Ta.

In other words, there is a problem that the fixed scroll end plate must be thickened when installing the injection port, and the efficiency improvement effect cannot be sufficiently obtained. The inventors found such a problem and came to constitute the subject matter of the present disclosure in order to solve the problem.

Therefore, the present disclosure provides a compressor with an injection mechanism in which an injection port can be installed without being restricted by increasing the thickness of the compression mechanism when configuring the injection port.

Hereinafter, embodiments will be described in detail with reference to the drawings. However, more detailed description than necessary may be omitted. For example, detailed descriptions of well-known matters or redundant descriptions of substantially the same configurations may be omitted. This is to avoid the following description from becoming more redundant than necessary and to facilitate understanding by those skilled in the art.

It should be noted that the accompanying drawings and the following description are provided to allow those skilled in the art to fully understand the present disclosure and are not intended to limit the claimed subject matter thereby.

(Embodiment 1)
Embodiment 1 will be described below with reference to FIGS. 1 to 8. FIG.

[1-1. composition]
FIG. 1 is a vertical cross-sectional view of a scroll-type compressor with an injection mechanism according to an embodiment of the present disclosure, and FIG. 2 is an enlarged cross-sectional view of the main part of the compression mechanism shown in FIG. The configuration and operation of the compressor with an injection mechanism according to the present embodiment will be described below.

As shown in FIG. 1, the compressor with an injection mechanism according to the present embodiment includes a sealed container 1, a compression mechanism section 2 located inside the sealed container 1, and a motor section 3 for driving the compression mechanism section 2. , and an oil reservoir 20 provided at the bottom of the closed container 1 . As shown in FIG. 2, the compression mechanism 2 includes a main bearing member 11 fixed in the closed container 1 by welding or shrink fitting, bolted onto the main bearing member 11, and a spiral wrap is attached to the end plate. An upright fixed scroll 12, an orbiting scroll 13 having an upright spiral wrap on an end plate, a compression chamber 15 formed by meshing the fixed scroll 12 and the orbiting scroll 13, and pressing the orbiting scroll 13 against the fixed scroll 12. and a back pressure chamber 29 for holding the pressure.

Between the orbiting scroll 13 and the main bearing member 11, there is provided a rotation restraining mechanism 14 such as an Oldham ring that prevents the orbiting scroll 13 from rotating and guides the orbiting scroll 13 to move in a circular orbit.

The shaft 4 is rotationally driven by the motor section 3 . The shaft 4 is supported by a main bearing member 11 and eccentrically drives an orbiting scroll 13 with an eccentric shaft portion 4 a at the upper end of the shaft 4 .

As a result, the orbiting scroll 13 is moved in a circular orbit. The compression chamber 15 formed between the fixed scroll 12 and the orbiting scroll 13 moves from the outer peripheral side toward the central portion while contracting the volume, and a suction pipe 16 leading to the outside of the sealed container 1 is used. A working fluid (hereinafter referred to as refrigerant) is sucked from a suction port 17 on the outer periphery of the fixed scroll 12, confined in a compression chamber 15, and then compressed. Refrigerant that reaches a predetermined pressure pushes open the discharge valve 19 from the discharge port 18 provided in the center of the fixed scroll 12, and flows from the discharge chamber 31 into which the refrigerant that has reached the discharge pressure is discharged, and further flows into the discharge refrigerant passage. 59, through the internal space 7, and finally out of the sealed container 1 from the discharge pipe 22.

A pump 25 is provided at the lower end of the shaft 4 , and the suction port of the pump 25 is positioned within the oil reservoir 20 . Since the pump 25 is driven simultaneously with the orbiting scroll 13, the pump 25 can reliably suck up the oil 6 in the oil reservoir 20 regardless of pressure conditions and operating speed. This will prevent the oil from running out.

The oil 6 sucked up by the pump 25 is supplied to the compression mechanism portion 2 through an oil supply hole 26 passing through the shaft 4 . By removing foreign matter from the oil 6 with an oil filter or the like before or after the oil 6 is sucked up by the pump 25, contamination of the compression mechanism 2 with foreign matter can be prevented, and reliability can be further improved.

The oil 6 led to the compression mechanism 2 has substantially the same discharge pressure as the scroll compressor, and also serves as a back pressure source for the orbiting scroll 13 . Further, part of the oil 6 enters the fitting portion between the eccentric shaft portion 4a and the orbiting scroll 13 and the bearing portion 66 between the shaft 4 and the main bearing member 11, seeking a place of escape by the supply pressure and its own weight. After lubricating each part, it falls and returns to the oil reservoir 20. - 特許庁

3 is a view taken along line CC of FIG. 2. FIG. The compression chamber 15 formed by the fixed scroll 12 and the orbiting scroll 13 includes an outer compression chamber 15a positioned outside the wrap of the orbiting scroll 13 and an inner compression chamber 15b positioned inside the wrap. The injection mechanism-equipped compressor 91 is an asymmetric scroll compressor in which the suction confinement volume of the outer compression chamber 15a and the suction confinement volume of the inner compression chamber 15b are different. Here, the suction confinement volume is the compression chamber volume immediately after the refrigerant sucked from the suction port 17 is confined.

By using an asymmetric scroll compressor, the suction confinement volume of the compressor as a whole increases, so the space inside the compressor can be used efficiently. In addition, since the refrigerant sucked from the suction port 17 can be confined in the vicinity of the suction port 17 in the outer compression chamber 15a and enter the compression process, the low-pressure, low-temperature refrigerant is heated by the compression mechanism 2, and the density of the refrigerant increases. It is possible to suppress the occurrence of deterioration.

On the other hand, the difference in suction confinement volume of each compression chamber affects the volume ratio. Volume ratio is the ratio of compression chamber volume during the compression stroke to suction containment volume. A volume ratio can be defined for each of the outer compression chamber and the inner compression chamber. Generally, when the inner compression chamber and the outer compression chamber communicate with the discharge port 18 provided in the central portion of the fixed scroll 12, the compression chamber volumes are substantially equal. If the discharge port 18 is the only discharge path for refrigerant in the compression chambers, the dischargeable volume ratio of each compression chamber is determined by the suction confined volume. Here, the dischargeable volume ratio is the ratio of the suction confined volume to the volume of the compression chamber when the compression chamber becomes capable of discharging, that is, when the compression chamber communicates with the discharge chamber 31 . A dischargeable volume ratio can be defined for each of the outer compression chamber and the inner compression chamber. Since the suction confinement volume of the outer compression chamber 15a is larger than the suction confinement volume of the inner compression chamber 15b, the compression stroke of the outer compression chamber 15a is longer than that of the inner compression chamber 15b, and the dischargeable volume ratio is increased. .

During low compression ratio operation, which is operation in a state where the compression ratio is relatively low, the compression chamber with a large dischargeable volume ratio cannot discharge the refrigerant in the compression chamber even if the pressure in the compression chamber exceeds the discharge pressure, resulting in an overcompression state. However, the outer compression chamber 15a is more easily overcompressed than the inner compression chamber 15b. Here, the compression ratio is the ratio of discharge pressure to suction pressure. In addition, the outer compression chamber 15a has a larger projected area when viewed in the pressing direction than the inner compression chamber 15b. Therefore, the excessively compressed state of the outer compression chamber 15 a tends to increase the force pushing the orbiting scroll 13 away from the fixed scroll 12 .

Moreover, based on the results of measuring the temperature distribution during operation, the wrap tip 13c of the orbiting scroll 13 gradually increases in wrap height from the winding start portion, which is the central portion, to the winding end portion, which is the outer peripheral portion. A slope shape is provided so that the This makes it possible to absorb dimensional changes due to thermal expansion and prevent local sliding.

As shown in FIG. 2, the scroll compressor includes a connection path 55-1 and a supply path 55-2 as an oil supply path 55 that guides oil from the oil reservoir 20 to the compression chamber 15. As shown in FIG. Further, as an oil supply route to the compression chamber 15, a passage 13a formed inside the orbiting scroll 13 and a recess 12a formed in the end plate of the fixed scroll 12 on the wrap surface side are provided. The passage 13a includes a supply passage 55-2.

One open end 55-2b of the passage 13a is formed at the wrap tip 13c and periodically opens into the recess 12a in accordance with the turning motion. Also, the other open end 55-2a of the passage 13a always opens into the back pressure chamber 29. As shown in FIG. As a result, the back pressure chamber 29 intermittently communicates only with the inner compression chamber 15b and does not communicate with the outer compression chamber 15a. In addition, by positively supplying oil to the inner compression chamber 15b having a high rate of pressure rise, the inner compression chamber 15b-1 (see FIG. 3) formed one before in the compression process and the inner compression chamber 15b-1 (see FIG. 3) formed next Leakage to the inner compression chamber 15b-2 (see FIG. 3) can be suppressed.

Further, as shown in FIG. 2, a seal member 78, a high-pressure region 30 that retains the refrigerant at the discharge pressure, and a back pressure region 30 that retains the refrigerant at an intermediate pressure between the discharge pressure and the suction pressure are provided on the back surface 13e of the orbiting scroll 13. A chamber 29 is provided. The sealing member 78 partitions the inner side of the sealing member 78 into the high pressure region 30 and the outer side of the sealing member 78 into the back pressure chamber 29 .

At least one of the oil supply routes is configured to pass through the back pressure chamber 29 . That is, the oil supply path 55 is composed of a connection path 55-1 from the high pressure region 30 to the back pressure chamber 29 and a supply path 55-2 from the back pressure chamber 29 to the inner compression chamber 15b. As a result, the orbiting scroll 13 is stably pressed against the fixed scroll 12 by the back pressure from the back surface 13e, thereby reducing leakage of refrigerant from the back pressure chamber 29 to the compression chamber 15 and stably operating the compressor. can.

Further, by using the seal member 78, the pressure in the high pressure region 30 and the pressure in the back pressure chamber 29 (hereinafter referred to as back pressure) are completely separated, and the pressure application from the back surface 29e of the orbiting scroll 29 can be stably controlled.

Further, by providing the connection path 55-1 from the high pressure region 30 to the back pressure chamber 29, the oil 6 can be supplied to the sliding portion of the rotation restraint mechanism 14 and the thrust sliding portion of the fixed scroll 12 and the orbiting scroll 13. .

Also, by providing the supply path 52 from the back pressure chamber 29 to the inner compression chamber 15b, the amount of oil supplied to the inner compression chamber 15b can be positively increased, and leakage loss in the inner compression chamber 15b can be suppressed.

One open end 55-1b of the connection path 55-1 is formed on the back surface 13e of the orbiting scroll 13 to allow the seal member 78 to travel therethrough, and the other open end 55-1a is always open to the high pressure region 30. FIG. Thereby, intermittent oil supply and adjustment of back pressure can be realized.

First, intermittent oil supply will be explained.

FIG. 5 is an explanatory view showing the positional relationship between the communication passage with the back pressure chamber and the seal member accompanying the revolving motion of the scroll compressor. In FIG. 5, the phase is shifted by 90 degrees, (a) 0 ° to 90 °, (b) 90 ° to 180 °, (c) 180 ° to 270 °, (d) 270 ° to 360 ° is shown. That is, FIG. 5(b) shows a state in which the shaft 4 has rotated 90 degrees from FIG. 5(a), FIG. 5(c) shows a state in which the shaft 4 has rotated from FIG. , a state rotated by 90 degrees from FIG. 5(c), and FIG. 5(a) shows a state rotated by 90 degrees from FIG. 5(d). As shown in FIG. 5, one open end 55-1b of the connection path 55-1 is positioned on the back surface 13e of the orbiting scroll 13. As shown in FIG. A back surface 13 e of the orbiting scroll 13 is partitioned into an inner high pressure area 30 and an outer back pressure chamber 29 by a seal member 78 . In the state of FIG. 5(b), one open end 55-1b is open to the back pressure chamber 29, which is outside the seal member 78, so that the back pressure chamber 29 and the high pressure region 30 communicate with each other. As a result, the oil 6 is supplied from the high pressure region 30 to the back pressure chamber 29 . 5(a), (c), and (d), the open end 55-1b is open inside the seal member 78, so the back pressure chamber 29 does not communicate with the high pressure region 30. FIG. Therefore, the oil 6 is not supplied from the high pressure region 30 to the back pressure chamber 29 .

That is, one open end 55-1b of the connection path 55-1 travels back and forth between the high pressure region 30 and the back pressure chamber 29, and a pressure difference is generated between the two open ends 55-1a and 55-1b of the connection path 55-1. The oil 6 is supplied to the back pressure chamber 29 only when this occurs. As a result, the amount of oil to be supplied can be adjusted according to the time ratio during which one open end 55-1b moves back and forth through the seal member 78. As shown in FIG. Therefore, the passage diameter of the connecting passage 55-1 can be configured to be 10 times or more the diameter of the oil filter.

In addition, since there is no danger of clogging the passage due to foreign matter getting caught in it, the lubrication of the thrust sliding portion and the rotation restraint mechanism 14 can be maintained in good condition at the same time as the application of stable back pressure, resulting in high efficiency and high reliability. realizable. The other open end 55-1a is always in the high pressure region 30, and the one open end 55-1b moves back and forth between the high pressure region 30 and the back pressure chamber 29. 1a moves back and forth between the high pressure region 30 and the back pressure chamber 29, and one of the open ends 55-1b is always in the back pressure chamber 29. Lubrication can be realized and the same effect can be obtained.

Next, the adjustment of the back pressure will be explained.

FIG. 4 is an open state diagram of the communication passage with the back pressure chamber and the injection port accompanying the orbital motion of the scroll compressor. FIG. 4 shows a state in which the orbiting scroll 13 is meshed with the fixed scroll 12 and viewed from the back surface 13e of the orbiting scroll 13, with phases shifted by 90 degrees. Similar to FIG. 5, FIG. 4 shows (a) 0° to 90°, (b) 90° to 180°, (c
) 180° to 270° and (d) 270° to 360°. 4(b) shows a state in which the shaft 4 is rotated 90 degrees from FIG. 4(a), FIG. 4(c) shows a state in which the shaft 4 is further rotated 90 degrees from FIG. , a state rotated by 90 degrees from FIG. 4(c), and FIG. 4(a) shows a state rotated by 90 degrees from FIG. 4(d).

The state shown in FIG. 4A is the position where the outer compression chamber 15a confines the refrigerant, and the state shown in FIG. 4C is the position where the inner compression chamber 15b confines the refrigerant.

In the state shown in FIG. 4(a), two outer compression chambers 15a are formed. The compression chamber 15a is in an intermediate pressure state. In the state shown in FIG. 4(c), the outer compression chamber 15a formed on the inner peripheral side is in a high pressure state before discharge.

In the state shown in FIG. 4(c), two inner compression chambers 15b are formed. The compression chamber 15b is in an intermediate pressure state. In the state shown in FIG. 4(d), the inner compression chamber 15b formed on the inner peripheral side is in a high pressure state before discharge.

The injection port 43 is shown in FIGS. 4(a), 4(b), 4(c) and 4(d), and this injection port 43 is located in the compression chamber in a state where the suction stroke is completed and compression is started. It is designed to open. This suppresses expansion of the injected intermediate-pressure refrigerant to the low-pressure suction port 17, increases the amount of refrigerant circulating in the refrigerating cycle, and enables high-capacity, high-efficiency operation. In order to realize such operation more effectively, the injection port 43 must necessarily be provided at a position close to the discharge port 18 and the discharge bypass port 21, and the discharge chamber 31 and the intermediate pressure path 41 must be compatible. It becomes difficult to partition by That is, when a member such as the discharge valve 19 that regulates the movable range of the discharge valve movable body is arranged independently and the discharge chamber 31 and the intermediate pressure path 41 are separated by separate members, a space is provided between the respective members. The injection port 43 could not be arranged in the vicinity of the discharge valve 19 because it would be necessary to arrange it.

Therefore, in the present embodiment, the partitioning member 44 itself that partitions the discharge chamber 31 and the intermediate pressure path 41 has a role of regulating the movable amount of the discharge valve 19, thereby making the injection port 43 closer to the discharge port 18. Can be configured in position.

7 is a view taken along line AA of FIG. 2. FIG. 8 is a view taken along line BB of FIG. 7. FIG.

The intermediate pressure path 41 provided inside the end plate of the fixed scroll 12 is also formed in a space surrounded by the fixed scroll 12 and the partitioning member 41 through the check valve 42 . By also regulating the lift amount of the discharge valve 19 provided in the immediate vicinity, the injection port 43 and the discharge port 18 are arranged close to each other.

By using a part of the partition member 41 as a regulating member for the discharge valve 19 in this manner, it is possible to share the fastening portion, reduce or eliminate the interference avoidance gap, and secure the length of the pressure seal. We have realized a compressor with an injection mechanism that can maximize the effect of the injection cycle by enabling the configuration of the injection port at a position close to.

Next, the action of the back pressure chamber 29 will be described. In the state of FIG. 4(d), one open end 55-2b opens into the recess 12a. Therefore, the inner compression chamber 15 b communicates with the back pressure chamber 29 . During high compression ratio operation, the oil 6 is supplied from the back pressure chamber 29 to the inner compression chamber 15b through the supply passage 55-2 and the passage 13a.

The recess 12a is provided at a position where one open end 55-2b opens immediately after the inner compression chamber 15b confines the sucked refrigerant (see FIG. 4(d)). In other words, one open end 55-2b of the oil supply path is provided at a position where it opens to the inner compression chamber 15b during the compression process after the drawn refrigerant is confined. Therefore, the pressure of the back pressure chamber 29 while communicating with the inner compression chamber 15b becomes substantially equal to the pressure of the inner compression chamber 15b. On the other hand, in the states of FIGS. 4(a), (b), and (c), one open end 55-2b does not open into the recess 12a. Therefore, the oil 6 is not supplied from the back pressure chamber 29 to the inner compression chamber 15b. Also, the pressure in the back pressure chamber 29 is not affected by the inner compression chamber 15b.

5(b) corresponding to FIG. 4(b), the back pressure chamber 29 and the high pressure region 30 communicate with each other. is shared to the back pressure chamber 29, and the pressure in the back pressure chamber 29 rises.

That is, the pressure in the back pressure chamber 29 can be adjusted to an intermediate pressure state between the suction pressure and the discharge pressure, and this pressure functions as a pressing force to the orbiting scroll.

The scroll compressor is provided with a discharge bypass port 21 in addition to the discharge port 18 as a passage for guiding the refrigerant compressed in the compression chamber 15 to the discharge chamber 31 . The discharge bypass port 21, like the discharge port 18, has a reed valve. When the pressure in the compression chamber 15 reaches the pressure in the discharge chamber 31 , the reed valve is pushed open and the refrigerant is discharged to the discharge chamber 31 . The maximum lift amount of the reed valve 19, which is the discharge valve movable body, is limited by the partition member 44, which is the movable body regulating member, to prevent damage due to excessive deformation. In particular, under operating conditions where the injection rate is high, the pressure rise speed in the compression chamber 15 also increases, so the load applied to the reed valve 19 increases, and the importance of regulating the lift amount increases.

Also, when the pressure in the compression chamber 15 is less than the pressure in the discharge chamber 31 , the reed valve is closed to prevent the refrigerant from flowing back from the discharge chamber 31 to the compression chamber 15 .

However, as a condition for the discharge port 18 and the discharge bypass port 21 to realize the functions described above, the compression chamber 15 must exist at a position communicating with the discharge port 18 and the discharge bypass port 21 . The discharge port 18 and the discharge bypass port 21 are fixed passages provided in the end plate of the fixed scroll 12 . The compression chamber 15 moves toward the center while reducing its volume along with the compression operation. can be discharged to The discharge bypass port 21 is provided to allow communication between the compression chamber 15 and the discharge chamber 31 before the compression chamber 15 communicates with the discharge chamber 31 through the discharge port 18 in the compression process.

The scroll compressor 91 has separate discharge bypass ports 21a and 21b, respectively, with which the outer compression chamber 15a communicates and the inner compression chamber 15b communicates.

The discharge bypass port 21a does not communicate with the outer compression chamber 15a in the state of FIG. 4(a), and communicates with the outer compression chamber 15a located on the outer peripheral side in the states of FIGS. 4(b) to 4(d). is provided in The discharge bypass port 21b does not communicate with the inner compression chamber 15 in the state of FIG. 4(d), and communicates with the inner compression chamber 15b located on the outer peripheral side in the states of FIGS. 4(a) to 4(c). is provided in

The outer compression chamber 15a completes the suction stroke at the timing shown in FIG. 4(a) and closes the outer compression chamber 15a. In FIG. 4B, when the compression stroke has progressed by 90°, the outer compression chamber 15a is already in communication with the discharge bypass port 21a. In this case, the dischargeable volume ratio of the outer compression chamber 15a is determined by the ratio of the intake confined volume of the outer compression chamber 15 to the compression chamber volume at the timing when the outer compression chamber 15a communicates with the discharge bypass port 21a. It does not depend on the communication timing with the port 18.

On the other hand, the inner compression chamber 15b completes the suction stroke at the timing shown in FIG. 4(c) and closes the inner compression chamber 15b. The inner compression chamber 15b does not communicate with the discharge bypass port 21b in FIG. 4(d) when the compression stroke has progressed 90 degrees, and communicates with the discharge bypass port 21b in FIG. 4(a) when the compression process has progressed further 90 degrees. do. Further, the inner compression chamber 15b communicates with the back pressure chamber 29 through the supply passage 55-2 and the passage 13a at the timing shown in FIG. 4(d).

In this case also, the dischargeable volume ratio of the inner compression chamber 15b is determined by the communication timing with the discharge bypass port 21b, and the dischargeable volume ratio of the inner compression chamber 15b to which the back pressure chamber 29 communicates is determined by the volume when the back pressure chamber is closed. ratio and the dischargeable volume ratio of the outer compression chamber 15a. Here, the volume ratio when the back pressure chamber is closed refers to the time when the communication between the back pressure chamber 29 and the inner compression chamber 15b, which is in the middle of compression, ends in the compression chamber on the side to which the back pressure chamber 29 communicates, that is, the inner compression chamber 15b. It is the ratio of the suction confinement volume to the volume of the inner compression chamber 15b on the outer peripheral side (that is, the timing immediately after FIG. 4(d)).

Next, a refrigeration cycle apparatus using the compressor with the injection mechanism will be described.

FIG. 6 is a refrigeration cycle diagram using a compressor with an injection mechanism according to an embodiment of the present invention.

As shown in FIG. 6, a refrigeration cycle apparatus using a compressor with an injection mechanism includes a compressor 91 with an injection mechanism, a condenser 92, an evaporator 93, two pressure reducers 94a and 94b, an injection pipe 95, and a gas-liquid separator. A vessel 96 is provided. A compressor 91 with an injection mechanism, a condenser 92, an upstream decompressor 94a, a gas-liquid separator 96, and a downstream decompressor 94b are annularly connected by piping. The injection pipe 95 connects the gas-liquid separator 96 and the compressor 91 with an injection mechanism.

The refrigerant condensed by the condenser 92 is decompressed to an intermediate pressure by the upstream decompressor 94 a and flows into the gas-liquid separator 96 . The gas-liquid separator 96 separates the intermediate pressure refrigerant into a gas phase component (gas refrigerant) and a liquid phase component (liquid refrigerant). The intermediate-pressure liquid refrigerant passes through the pressure reducer 94b on the further downstream side and flows into the evaporator 93 as a low-pressure refrigerant.

The liquid refrigerant that has flowed into the evaporator 93 evaporates through heat exchange and is discharged as gas refrigerant or gas refrigerant partially mixed with liquid refrigerant. The refrigerant discharged from the evaporator 93 flows into the compression chamber 15 of the compressor 91 with an injection mechanism.

On the other hand, the intermediate-pressure gas refrigerant separated by the gas-liquid separator 96 passes through the injection pipe 95 and is injected into the compression chamber 15 in the compressor 91 with an injection mechanism. The injection pipe 95 may be provided with a blocking valve or a decompressor to adjust and stop the injection pressure.

In the compression process of compressing the low-pressure refrigerant flowing from the evaporator 93, the injection-equipped compressor 91 injects the intermediate-pressure refrigerant of the gas-liquid separator 96 into the compression chamber 15, compresses the refrigerant, and converts it into a high-temperature, high-pressure refrigerant. It is discharged from the discharge pipe 22 to the condenser 92 .

The ratio of the gas phase component and the liquid phase component separated by the gas-liquid separator 96 will be described. The greater the pressure difference between the inlet side pressure and the outlet side pressure of the pressure reducer 94a on the upstream side, the greater the gas phase component. Also, the gas phase component increases as the degree of supercooling of the refrigerant at the outlet of the condenser 92 decreases or as the dryness thereof increases.

On the other hand, the amount of refrigerant sucked by the compressor with injection mechanism 91 through the injection pipe 95 increases as the intermediate pressure increases. When more refrigerant is sucked from the injection pipe 95 than the gas phase component ratio of the refrigerant separated by the gas-liquid separator 96 , the gas refrigerant in the gas-liquid separator 96 is exhausted and liquid refrigerant flows into the injection pipe 95 .

In order to maximize the performance of the injection-equipped compressor 91, it is desirable that the gas refrigerant separated in the gas-liquid separator 96 is completely sucked into the injection-equipped compressor 91 through the injection pipe 95. If the state of equilibrium is deviated, the liquid refrigerant flows from the injection pipe 95 into the compressor 91 with an injection mechanism. It is desirable that the injection mechanism-equipped compressor 91 maintains high reliability even when the liquid refrigerant flows from the injection pipe 95 .

7 is a view taken along line AA of FIG. 2. FIG. 8 is a view taken along line BB of FIG. 7. FIG.

As shown in FIGS. 1, 2, 7, and 8, the intermediate-pressure refrigerant flowing from the injection pipe 95 flows into the intermediate-pressure path 41 and flows into the reed valve of the check valve 42 provided in front of the injection port 43. 42a is opened, the refrigerant is injected into the closed compression chamber 15, and together with the refrigerant sucked from the suction port 17, flows from the discharge port 18 or the discharge bypass port 21 to the discharge chamber 31, and further through the discharge refrigerant passage 59 into the sealed container 1. is discharged into the internal space 7 and finally sent out from the discharge pipe 22 .

An injection port 43 for injecting intermediate-pressure refrigerant is provided through the end plate of the fixed scroll 12 . The injection port 43 opens sequentially to the outer compression chamber 15a and the inner compression chamber 15b. As shown in FIG. 4, the injection port 43 is provided at a position where it opens during the compression process after being confined in the outer compression chamber 15a and the inner compression chamber 15b.

In the compressor with an injection mechanism according to the present embodiment, the check valve 42 is constructed by assembling the reed valve 42a to the valve seat 42b provided on the end plate of the fixed scroll 12 and sandwiching the reed valve 42a between the partition members 44. The maximum lift amount is regulated by the check valve movable body regulating portion 44b.

The reed valve 42 a opens to communicate with the compression chamber 15 only when the internal pressure of the compression chamber 15 is lower than the pressure on the injection pipe 95 side of the check valve 42 of the intermediate pressure path 41 . By using the reed valve 42a, the number of sliding portions in the movable portion is reduced, the sealing performance can be maintained for a long period of time, and the flow passage area can be easily expanded as necessary. If the check valve 42 is not provided or if the check valve 42 is provided in the injection pipe 95, the refrigerant in the compression chamber 15 flows back to the injection pipe 95, resulting in wasted compression power consumption. In the present embodiment, the check valve 42 is provided near the compression chamber 15 to suppress backflow from the compression chamber 15 .

As shown in FIG. 7, the discharge valve 19, the discharge bypass reed valve 21a, and the reed valve 42a of the check valve are made of a single sheet material. It is integrally fixed with a bolt 48 while restricting the maximum lift amount of the valve. As a result, the number of fixing members 48 can be reduced and the injection port 43 can be arranged at a position closer to the discharge valve 19 .

In addition, as shown in FIG. 4, the injection port 43 is provided at a position that sequentially opens to the first compression chamber 15a and the second compression chamber 15b. 4(b) and 4(c), the injection port 43 closes the suctioned refrigerant as shown in the outer compression chamber 15a or FIG. The end plate of the fixed scroll 12 is provided so as to penetrate the end plate of the fixed scroll 12 at a position where it opens to the inner compression chamber 15b during the compression stroke after loading. This prevents the refrigerant injected from the injection port 43 from flowing out from the compression chamber before closing to the suction port 17 and reducing the amount of refrigerant that should be originally sucked from the evaporator 93 .

In this embodiment, the oil supply path is used as the communication path between the compression chamber and the back pressure chamber, but the same effect can be obtained by providing an independent path in addition to the oil supply path. Further, the back pressure chamber is not limited to the back side of the orbiting scroll, but may be provided on the back side of the fixed scroll to press the fixed scroll against the orbiting scroll.

Furthermore, in the present embodiment, a scroll-type compressor with an injection mechanism is used, but similar effects can be obtained by using other compression systems such as a rotary system, a reciprocating system, and a screw system.

(Other embodiments)
As described above, Embodiment 1 has been described as an example of the technology disclosed in the present application. However, the technology in the present disclosure is not limited to this, and can also be applied to embodiments with modifications, replacements, additions, omissions, and the like. Also, it is possible to combine the constituent elements described in the first embodiment to form a new embodiment.

Therefore, other embodiments will be exemplified below.

In the first embodiment, the intermediate pressure path 41 is formed in the end plate of the fixed scroll 12, and the check valve 42a is pushed open from the intermediate pressure path 41 to open the intermediate pressure path between the upper surface of the fixed scroll 12 and the partition member 44. Although the flow is configured to flow from the portion 41 to the injection port 43 and the check valve movable body restricting portion 44b is provided in the partitioning member 44, this can also be configured as follows. That is, as shown in FIG. 9, a dividing member 44 is installed on the upper surface of the fixed scroll 12 to form an intermediate pressure passage 41 therein, and the intermediate pressure passage 41 is recessed on the upper surface of the fixed scroll 12 to form an injection pipe. The intermediate-pressure refrigerant introduced from 95 may pass through the interior of the partitioning member 44 , push open the check valve 42 a provided on the valve seat 42 b of the partitioning member 44 , and flow to the injection port 43 . By adopting such a configuration, the end plate of the fixed scroll 12 can be made thinner, and the lengths of the discharge port 18 and the injection port 43 are shortened to suppress the generation of dead volume, resulting in a highly efficient compressor with an injection mechanism. can be

[1-2. effects, etc.]
As described above, in the present embodiment, in the compressor with an injection mechanism, the working fluid in an intermediate pressure state between a low pressure and a high pressure is supplied from the outside of the sealed container to the compression chamber via the injection pipe in the compression mechanism. and an intermediate pressure path for drawing in the discharge valve, and at least one of partitioning members that partition the discharge chamber and the intermediate pressure path restricts the movable range of the discharge valve. As a result, since the partition member also plays the role of a regulating member for the discharge valve, injection can be performed near the discharge port that is opened and closed by the discharge valve without increasing the thickness of the compression mechanism or considering interference during assembly. A port can be installed, and a high-capacity, high-efficiency compressor with an injection mechanism can be provided. In addition, since the discharge valve fixing portion can be used as a pressure seal portion of the dividing member, restrictions on the position of the injection port can be greatly relaxed.

In addition, since the injection port, which is the opening to the compression chamber in the intermediate pressure path, is provided at a position where it opens only to the compression chamber after the compression is started, interference with the discharge valve is a problem. It is possible to provide a high-capacity and high-efficiency compressor with an injection mechanism. That is, in order to open the injection port only to the compression chamber after the start of compression, it is necessary to position the injection port closer to the discharge valve. According to the invention, such a problem can be avoided, and a high-capacity and high-efficiency compressor with an injection mechanism can be provided.

In addition, a check valve is provided between the compression chamber and the intermediate pressure path to suppress backflow of the working fluid, and the partition member is provided with a valve seat of the check valve. It is possible to suppress the backflow of the working fluid from to the intermediate pressure path and reduce the dead volume of the compression chamber. In addition, by using the valve seat of the check valve as the partition member, the space can be saved, the influence on the intermediate pressure path can be minimized, and high-capacity and high-efficiency operation can be achieved.

Further, a check valve is provided between the compression chamber and the intermediate pressure path to suppress backflow of the working fluid, and the movable range of the movable body of the check valve is restricted by the partitioning member. The backflow of the working fluid from the chamber to the intermediate pressure path can be suppressed, and the dead volume of the compression chamber can be reduced. In addition, by using the movable range regulating member of the movable body of the check valve as the partitioning member, the space can be saved, the influence on the intermediate pressure path can be minimized, and high-capacity and highly efficient operation is possible. .

Further, since a reed valve type valve body is used for the discharge valve and the check valve, and a plurality of valve bodies, including at least one each, are formed on a single sheet, the discharge chamber and the intermediate valve can be arranged in a plane. It becomes possible to partition the pressure path. That is, when fixing both the discharge valve movable body and the check valve movable body between the partition member and the compression mechanism section, if the thicknesses of the plurality of movable bodies differ, the thickness difference between the movable bodies is taken into consideration when determining the partition member. Although the shape had to be adjusted, by constructing the discharge valve and the check valve with a single sheet, dimensional control for fixing and pressure sealing becomes easy, and the seat member can be placed anywhere. , so that the discharge chamber and the intermediate pressure path can be partitioned in a plane. As a result, the discharge chamber and the intermediate pressure path can be easily divided, and a high-capacity, high-efficiency compressor with an injection mechanism can be provided without being restricted by the position of the injection port.

Although the embodiments of the technology in the present disclosure have been described above, the above-described embodiments are for illustrating the technology in the present disclosure. Substitutions, additions, omissions, etc. can be performed.

INDUSTRIAL APPLICABILITY The compressor with an injection mechanism of the present invention is a high-capacity and high-efficiency compressor, and is useful for cooling and heating air conditioning systems, refrigerators and other refrigeration systems, heat pump hot water supply systems, and the like.

1 Airtight Container 2 Compression Mechanism Part 3 Motor Part 4 Shaft 4a Eccentric Shaft Part 6 Oil 7 Internal Space 11 Main Bearing Member 12 Fixed Scroll 12a Recess 13 Orbiting Scroll 13c Wrap Tip 13e Back 14 Rotation Restraining Mechanism 15 Compression Chamber 15a Outer Compression Chamber 15b Inner Compression Chamber 16 Suction Pipe 17 Suction Port 18 Discharge Port 19 Discharge Valve (Discharge Valve Movable Body)
20 oil reservoir 21 discharge bypass port 21a discharge bypass reed valve 22 discharge pipe 25 pump 26 oil supply hole 29 back pressure chamber 30 high pressure region 31 discharge chamber 41 intermediate pressure path 42 check valve 42a reed valve 42b valve seat 43 injection port 43a injection Port entrance 44 Partitioning member (movable body restricting member)
44a Discharge valve movable body restricting portion 44b Check valve movable body restricting portion 45 Muffler 48 Fixing member (bolt)
55 Oil supply path 55-1 Connection path 55-1a The other open end (high pressure area side)
55-1b One open end (back pressure chamber side)
55-2 Supply path 55-2a Other open end (back pressure chamber side)
55-2b One open end (compression chamber side)
59 Discharged refrigerant passage 66 Bearing 78 Seal member 91 Compressor with injection mechanism 92 Condenser 93 Evaporator 94 Expansion valve 95 Injection pipe 96 Gas-liquid separator

Claims (3)

A compression mechanism section is provided inside the sealed container to suck working fluid in a low-pressure state and compress it to a high-pressure state, and the compression mechanism section is provided with a discharge valve at the outlet from the compression chamber to the discharge chamber to prevent backflow. In a compressor with
The compression mechanism section is provided with an intermediate pressure path for drawing working fluid in an intermediate pressure state between low pressure and high pressure from the outside of the closed container into the compression chamber,
A check valve is provided to suppress reverse flow of the working fluid from the compression chamber to the intermediate pressure path,
regulating a movable range of the discharge valve by at least one of partitioning members that partition the discharge chamber and the intermediate pressure path ;
The partition member is provided with a valve seat of the check valve,
A compressor with an injection mechanism, wherein a reed valve type valve body is used for each of the discharge valve and the check valve, and a plurality of the valve bodies including at least one of each valve body are formed on an integrated seat. A compression mechanism section is provided inside the sealed container to suck working fluid in a low-pressure state and compress it to a high-pressure state, and the compression mechanism section is provided with a discharge valve at the outlet from the compression chamber to the discharge chamber to prevent backflow. In a compressor with
The compression mechanism section is provided with an intermediate pressure path for drawing working fluid in an intermediate pressure state between low pressure and high pressure from the outside of the closed container into the compression chamber,
A check valve is provided to suppress reverse flow of the working fluid from the compression chamber to the intermediate pressure path,
regulating a movable range of the discharge valve by at least one of partitioning members that partition the discharge chamber and the intermediate pressure path ;
restricting the movable range of the movable body of the check valve by the partition member;
A compressor with an injection mechanism, wherein a reed valve type valve body is used for each of the discharge valve and the check valve, and a plurality of the valve bodies including at least one of each valve body are formed on an integrated seat. 3. The injection port of the intermediate pressure path, which is an opening to the compression chamber, is provided at a position that opens only to the compression chamber after compression is started. Compressor with injection mechanism.

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