JPWO2020157842A1 - Compressor and refrigeration cycle equipment - Google Patents

Abstract

The compressor includes a compression mechanism unit that compresses and discharges the refrigerant, a rotating shaft that rotates so as to transmit power to the compression mechanism unit, an electric motor that rotationally drives the rotating shaft, and an impeller provided on the rotating shaft. The flow path is provided with a flow path through which the refrigerant flows, and the flow path is formed with a spray port for blowing the refrigerant onto the impeller.

Description

The present invention relates to a compressor and a refrigeration cycle device including a compression mechanism, a rotating shaft, and an electric motor.

Conventionally, as described in Patent Document 1, there is known a method of gaining a condensing capacity by driving a fan installed in a unit by a turbine installed in a refrigerant circuit and cooling the refrigerant flow path.

Further, as described in Patent Document 2, it is known that the energy recovery efficiency of a unit is enhanced by using an expansion turbine in a unit circuit.

Japanese Unexamined Patent Publication No. 61-79955 Japanese Unexamined Patent Publication No. 2009-216090

However, although the technique of Patent Document 1 can obtain a cooling effect, there is a problem that a complicated system is required to control the cooling effect as a unit.

Further, in the technique of Patent Document 2, the expansion turbine is a so-called generator. There was a problem of increasing the cost of the unit by installing the expansion turbine system. In addition, there is a problem that control becomes complicated regarding the handling of generated energy.

An object of the present invention is to solve the above problems, and an object of the present invention is to provide a compressor and a refrigeration cycle device capable of controlling a cooling effect with a simple and inexpensive configuration.

The compressor according to the present invention includes a compression mechanism unit that compresses and discharges a refrigerant, a rotating shaft that rotates so as to transmit power to the compression mechanism unit, an electric motor that rotationally drives the rotating shaft, and the rotating shaft. The impeller provided in the above and a flow path through which the refrigerant flows are provided, and a spray port for spraying the refrigerant on the impeller is formed in the flow path.

The refrigeration cycle apparatus according to the present invention includes the above-mentioned compressor.

According to the compressor and the refrigeration cycle apparatus according to the present invention, an impeller is provided on the rotating shaft, and a spray port for spraying a refrigerant on the impeller is formed in the flow path. According to this, the impeller sprayed with the refrigerant from the spray port rectifies the sprayed refrigerant, and a cooling effect can be obtained in the compressor. Therefore, the cooling effect can be controlled with a simple and inexpensive configuration.

It is explanatory drawing which shows the vertical cross section of the compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing which shows the flow of the refrigerant gas in the compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing which shows the operating state of the impeller of the compressor which concerns on Embodiment 1 of this invention in the cross section of the line AA of FIG. It is explanatory drawing which shows the flow of the refrigerant gas in the compressor which concerns on the modification 1 of Embodiment 1 of this invention. It is explanatory drawing which shows the vertical cross section of the lower half body of the compressor which concerns on Embodiment 2 of this invention. It is explanatory drawing which shows the operating state of the reversing impeller of the compressor which concerns on Embodiment 2 of this invention in the cross section of the line BB of FIG. It is explanatory drawing which shows the vertical cross section of the compressor which concerns on Embodiment 4 of this invention. It is explanatory drawing which shows the vertical cross section of the compressor which concerns on Embodiment 5 of this invention. It is a refrigerant circuit diagram which shows the refrigerating cycle apparatus which applied the compressor which concerns on Embodiment 6 of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In each figure, those having the same reference numerals are the same or equivalent thereof, and they are common in the entire text of the specification. Further, in the cross-sectional view, hatching is omitted as appropriate in view of visibility. Furthermore, the forms of the components shown in the full text of the specification are merely examples and are not limited to these descriptions.

Embodiment 1.
<Compression 100>
FIG. 1 is an explanatory view showing a vertical cross section of the compressor 100 according to the first embodiment of the present invention. The compressor 100 shown in FIG. 1 is a high-pressure shell type scroll compressor. The compressor 100 includes a compression mechanism unit 50, a rotating shaft 60, and an electric motor 7. The compression mechanism portion 50, the rotating shaft 60, and the electric motor 7 are housed in the closed container 10. The compression mechanism unit 50 has a fixed scroll 1 and a swing scroll 2, and compresses and discharges the refrigerant. The rotation shaft 60 transmits power to the compression mechanism unit 50 and rotates so as to swing the swing scroll 2. The electric motor 7 rotationally drives the rotary shaft 60. Here, an example in which the rotating shaft 60 extends in the vertical direction is shown, but the present invention is not limited to this, and the rotating shaft 60 may be inclined and extended in the vertical direction.

The rotation shaft 60 extends along the vertical direction of the upper U and the lower D. The rotary shaft 60 has a swing shaft 61 above the U. The rotating shaft 60 has a main shaft 62 at the lower side D. The peripheral portion of the lower end of the rotary shaft 60 is refueled with refrigerating machine oil that lubricates various sliding portions by raising the central portion of the rotary shaft 60 upward U from the refueling pump 63 configured at the lower end of the rotary shaft 60. An oil reservoir 70 is formed. The compression mechanism portion 50 is provided on the upper end side of the rotating shaft 60.

The electric motor 7 is provided below D of the compression mechanism unit 50. The electric motor 7 is located above U above the oil reservoir 70. The electric motor 7 has a stator fixed to the inner wall surface of the closed container 10 and a rotor arranged on the center side of the stator and rotated by a stator that includes a permanent magnet and is energized. The rotor is attached to the spindle 62. A refrigerant flow path 7a penetrating in the vertical direction is formed in the rotor.

In the closed container 10, the high-pressure side of the upper space 10a, which is the refrigerant atmosphere after the refrigerant gas is compressed by the compression mechanism 50, is partitioned from the low-pressure side, which is the refrigerant atmosphere before flowing into the compression mechanism 50. A partition plate 21 in the vicinity of the fixed scroll 1 is arranged. The low-pressure side, which is the refrigerant atmosphere before flowing into the compression mechanism portion 50, is formed from the inflow pipe 11 to the suction chamber 14a. Therefore, the partition plate 21 partitions the upper space 10a and the lower space 10b in the closed container 10. The first high-pressure side, which is the refrigerant atmosphere after the refrigerant gas is compressed by the compression mechanism unit 50, is formed in the upper space 10a in the closed container 10. The second high-pressure side, which is the refrigerant atmosphere after the refrigerant gas is compressed by the compression mechanism unit 50 and the refrigerant atmosphere before being discharged from the compressor 100, is the closed container 10 below D of the compression mechanism unit 50. It is formed in the lower space 10b inside. That is, the inside of the closed container 10 is partitioned into two high-pressure side refrigerant atmospheres by the compression mechanism unit 50.

The outer peripheral portion of the fixed scroll 1 is fastened to the fixed frame 4 by bolts 16. Plate-shaped spiral teeth 1b are formed on the lower surface of the lower D of the base plate portion 1a of the fixed scroll 1. Further, on the outer peripheral portion of the lower surface of the lower D of the base plate portion 1a of the fixed scroll 1, two pairs of oldham guide grooves 1c are formed substantially in a straight line. A pair of fixed side keys 5a are reciprocally and slidably engaged with a pair of oldham guide grooves 1c by two of the oldam mechanisms 5.

Plate-shaped spiral teeth 2b are formed on the upper surface of the upper U of the base plate portion 2a of the rocking scroll 2. The plate-shaped spiral teeth 1b of the fixed scroll 1 and the plate-shaped spiral teeth 2b of the swing scroll 2 are combined so as to mesh with each other. A plurality of compression chambers 14b for compressing the refrigerant gas from the suction chamber 14a are formed between the combined plate-shaped spiral teeth 1b and the plate-shaped spiral teeth 2b. The plurality of compression chambers 14b suck the refrigerant gas from the suction chambers 14a existing on the outer periphery into the compression chambers 14b. The refrigerant gas sucked into the compression chamber 14b increases the pressure of the refrigerant gas as it moves toward the central portion. Then, the high-pressure refrigerant gas is discharged from the innermost chamber 14c formed in the central portion of the compression mechanism portion 50 into the upper space 10a in the closed container 10.

A hollow cylindrical boss portion 2c is formed in the center of the lower surface of the lower D on the side opposite to the upper surface on which the plate-shaped spiral teeth 2b are formed in the base plate portion 2a. A swing bearing 2d is formed on the inner surface of the boss portion 2c. The swing shaft 61 of the rotary shaft 60 is swingably fitted in the swing bearing 2d. Further, on the outer peripheral portion of the lower surface D, which is the same as the boss portion 2c on the side opposite to the upper surface on which the plate-shaped spiral teeth 2b are formed on the base plate portion 2a, the thrust receiver 3a of the movable frame 3 can be pressure-welded and slid. Thrust surface 2e is formed.

On the outer peripheral portion of the base plate portion 2a of the oscillating scroll 2, a pair of oldham guide grooves 2f having a phase difference of approximately 90 degrees from the oldam guide groove 1c of the fixed scroll 1 are formed substantially in a straight line. There is. A pair of swinging side keys 5b are reciprocally and slidably engaged with a pair of oldham guide grooves 2f by two of the oldam mechanisms 5.

A sliding surface 3b is formed on the outside of the thrust receiver 3a of the movable frame 3 so that the annular portion 5c of the oldham mechanism 5 slides when it reciprocates. At the center of the movable frame 3, a main bearing 3c that radially supports the main shaft 62 that is rotationally driven by the electric motor 7 is formed.

The upper space 10a and the lower space 10b in the closed container 10 are separated by a partition plate 21 installed in the vicinity of the fixed scroll 1. The upper space 10a and the lower space 10b are connected by a spray pipe 22. The spray pipe 22 is used as a main flow path for the refrigerant gas. The refrigerant gas compressed by the compression mechanism unit 50 is sent from the upper space 10a to the lower space 10b by the spray pipe 22. The refrigerant gas sent to the lower space 10b flows from the discharge pipe 12 to the refrigerant circuit. Here, the discharge pipe 12 is arranged so as to be fixed by inserting an inlet portion into the fixed frame 4 at a height in the vertical direction between the fixed frame 4 and the electric motor 7.

<Structure of impeller 30a>
An impeller 30a is provided on the main shaft 62 of the rotating shaft 60. The impeller 30a is provided between the electric motor 7 on the upper side U and the oil reservoir 70 on the lower side D. The impeller 30a disperses the blown refrigerant gas in the vertical direction while rotating the impeller 30a itself by blowing the refrigerant gas onto the blades from the outer peripheral side. The structure of the impeller 30a is a well-known structure in which a plurality of plate-shaped blades that receive wind are scattered on the outer peripheral portion. The impeller 30a is completely fixed to the rotating shaft 60. Therefore, the impeller 30a rotates by receiving the refrigerant gas on the plurality of blades of the impeller 30a itself by spraying the refrigerant gas from the outer peripheral side, and auxiliaryly rotationally drives the main shaft 62 of the rotating shaft 60.

The impeller 30a may be provided above the electric motor 7 so as to be completely fixed to the main shaft 62.

<Structure of spray port 22a>
The spray pipe 22 again flows the refrigerant gas once discharged to the outside of the closed container 10 from the upper space 10a on the first high pressure side of the closed container 10 into the lower space 10b on the second high pressure side of the closed container 10. A discharge flow path for circulating the refrigerant gas is configured so as to allow the refrigerant gas to flow. A spray port 22a for blowing the refrigerant gas onto the impeller 30a is formed at the downstream end portion inserted into the lower space 10b of the spray pipe 22. That is, the spray port 22a is formed at the tip of the spray pipe 22 which is a discharge flow path through which the refrigerant gas discharged from the compression mechanism unit 50 has flowed. The spray pipe 22 and the spray port 22a are one. The spray port 22a is installed at a position deviated from the central portion in the lower space 10b and at a height in the vertical direction of the impeller 30a.

<Operation of impeller 30a>
FIG. 2 is an explanatory diagram showing a flow of refrigerant gas in the compressor 100 according to the first embodiment of the present invention. FIG. 3 is an explanatory view showing an operating state of the impeller 30a of the compressor 100 according to the first embodiment of the present invention in a cross section of the line AA of FIG.

As shown in FIGS. 2 and 3, the refrigerant gas compressed by the compression mechanism unit 50 is sent to the lower space 10b by the spray pipe 22. The spray port 22a of the spray pipe 22 sprays the refrigerant gas so as to rotate the impeller 30a in the same direction as the rotation direction 80c of the rotation shaft 60. The refrigerant gas sprayed on the impeller 30a collides with a plurality of blades of the impeller 30a, rotates the impeller 30a itself, and is dispersed in the vertical direction.

The refrigerant gas dispersed from the impeller 30a to the upper U flows through the refrigerant flow path 7a of the motor 7 to the upper U and is discharged from the discharge pipe 12 to the outside of the compressor. In the vicinity of the discharge pipe 12 in the lower space 10b, the refrigerant gas is drawn into the discharge pipe 12, so that the pressure is lower than that on the lower U side of the lower space 10b. Therefore, the refrigerant gas in the lower space 10b smoothly flows upward U so as to be drawn into the discharge pipe 12. At this time, the refrigerant gas flowing upward in the refrigerant flow path 7a of the electric motor 7 cools the generated electric motor 7. Here, the temperature of the high-pressure refrigerant gas compressed by the compression mechanism unit 50 is about 120 ° C. On the other hand, the temperature of the heated motor 7 is about 130 ° C. Therefore, the cooling effect of the electric motor 7 can be obtained by the refrigerant gas flowing through the refrigerant flow path 7a of the electric motor 7.

On the other hand, the refrigerant gas dispersed downward from the impeller 30a wraps around toward the upper U on the low pressure side of the lower space 10b so as to be drawn into the discharge pipe 12. Then, the refrigerant flow path 7a of the electric motor 7 flows upward U and joins the refrigerant gas discharged from the discharge pipe 12. As a result, the refrigerant gas dispersed downward from the impeller 30a is dispersed by the impeller 30a, the flow rate of the refrigerant gas that agitates or soars the refrigerating machine oil is reduced, and the oil that flows out of the compressor rises. Is suppressed.

As shown in FIG. 3, the refrigerant gas sent from the upper space 10a to the lower space 10b by the spray pipe 22 flows out from the spray port 22a, so that the main shaft 62 rotates in the same rotation direction as 80c, which is rotated by the compressor operation. The impeller 30a fixed to the spindle 62 is rotated in the direction 80a. As a result, the impeller 30a is rotated by the flow of the refrigerant gas, the rotation of the spindle 62 is assisted in addition to the motor 7, the amount of input power of the compressor 100 to the motor 7 is reduced, and the compressor 100 with high performance is produced. can get.

<Modification example 1>
FIG. 4 is an explanatory diagram showing the flow of the refrigerant gas in the compressor 100 according to the first modification of the first embodiment of the present invention. In the first modification, the description of the same items as in the above embodiment will be omitted, and only the characteristic portion thereof will be described.

As shown in FIG. 4, the spray port 22a is formed at the downstream end portion of the discharge flow path 22c through which the refrigerant gas discharged from the compression mechanism unit 50 has flowed. Here, the discharge flow path 22c is formed in one flow path connecting the upper space 10a and the lower space 10b by using a pipe member, a space portion, or the like in the closed container 10.

<Effect of Embodiment 1>
According to the first embodiment, the compressor 100 includes a compression mechanism unit 50 that compresses and discharges the refrigerant. The compressor 100 includes a rotating shaft 60 that rotates so as to transmit power to the compression mechanism unit 50. The compressor 100 includes an electric motor 7 that rotationally drives the rotating shaft 60. The compressor 100 includes an impeller 30a provided on the rotating shaft 60. The compressor 100 includes a spray pipe 22 as a discharge flow path through which the refrigerant flows. The spray pipe 22 is formed with a spray port 22a for blowing the refrigerant gas onto the impeller 30a.

According to this configuration, the impeller 30a sprayed with the refrigerant gas from the spray port 22a rectifies the sprayed refrigerant gas, and a cooling effect can be obtained in the compressor 100. Therefore, the cooling effect can be controlled with a simple and inexpensive configuration.

According to the first embodiment, the rotating shaft 60 extends in the axial direction along the vertical direction. An oil reservoir 70 is formed around the lower end of the rotating shaft 60. The compression mechanism portion 50 is provided on the upper end side of the rotating shaft 60. The electric motor 7 is provided below D of the compression mechanism unit 50. The impeller 30a is provided between the electric motor 7 and the oil reservoir 70.

According to this configuration, the impeller 30a sprayed with the refrigerant gas from the spray port 22a disperses and rectifies the refrigerant gas sprayed vertically, and cools the motor 7 in the compressor 100 with the rising refrigerant gas. A cooling effect can be obtained. Further, the refrigerant gas sprayed by the impeller 30a can be dispersed in the vertical direction to suppress the generation of a turbulent swirling flow in the closed container 10, promote the separation of the refrigerant gas and the refrigerating machine oil, and the refrigerating machine oil becomes the refrigerant gas. At the same time, it is possible to suppress the oil rising that is taken out of the compressor.

According to the first embodiment, the spray port 22a sprays the refrigerant so that the impeller 30a rotates in the same rotation direction 80a as the rotation direction 80c of the rotation shaft 60.

According to this configuration, since the impeller 30a does not go against the rotation direction 80c of the rotating shaft 60, the impeller 30a can smoothly rotate together with the rotating shaft 60.

According to the first embodiment, there is only one spray port 22a.

According to this configuration, the strong refrigerant gas is blown from the spray port 22a to the impeller 30a, and the rectifying effect of the refrigerant gas can be improved.

According to the first embodiment, the impeller 30a is fixed to the rotating shaft 60.

According to this configuration, the refrigerant gas is sprayed from the spray port 22a, and the impeller 30a fixed to the rotating shaft 60 can apply an auxiliary driving force to the rotating shaft 60 in addition to the electric motor 7, and the driving force of the electric motor 7 can be applied. Auxiliary effect can be obtained. In particular, when the refrigerant is sprayed so that the spray port 22a rotates the impeller 30a in the same rotation direction 80a as the rotation direction 80c of the rotation shaft 60, the auxiliary effect of the driving force of the electric motor 7 can be more preferably obtained.

According to the first embodiment, the spray port 22a is formed at the tip of the spray pipe 22 or the discharge flow path 22c through which the refrigerant gas discharged from the compression mechanism unit 50 has flowed.

According to this configuration, the high-pressure refrigerant gas discharged from the compression mechanism unit 50 is blown to the impeller 30a from the spray port 22a, and the momentum of the refrigerant gas blown to the impeller 30a becomes stronger.

According to the first embodiment, the compressor 100 includes a closed container 10 in which the high-pressure side, which is the refrigerant atmosphere after the refrigerant gas is compressed by the compression mechanism unit 50, is divided into two. The spray pipe 22 as a discharge flow path is a pipe that allows the refrigerant gas once discharged from the first high-pressure side of the closed container 10 to the outside of the closed container 10 to flow into the second high-pressure side of the closed container 10 again. be.

According to this configuration, in the high-pressure shell type scroll compressor, the high-pressure refrigerant gas discharged from the compression mechanism unit 50 is sprayed from the spray port 22a to the impeller 30a via the spray pipe 22.

Embodiment 2.
FIG. 5 is an explanatory view showing a vertical cross section of the lower half of the compressor 100 according to the second embodiment of the present invention. FIG. 6 is an explanatory view showing an operating state of the reversing impeller 30b of the compressor 100 according to the second embodiment of the present invention in a cross section of the line BB of FIG. In the second embodiment, the description of the same items as those in the above-described embodiment will be omitted, and only the characteristic portion thereof will be described.

As shown in FIGS. 5 and 6, the impeller 30a is rotatable with respect to the rotating shaft 60. Further, the rotating shaft 60 is provided with a reversing impeller 30b on the lower D side in the vicinity of the impeller 30a. The reversing impeller 30b is rotatable with respect to the rotating shaft 60. The structure of the reversing impeller 30b is known in the past, such as a plurality of plate-shaped blades that receive wind scattered on the outer peripheral portion. As a method of rotatably attaching the impeller 30a and the reversing impeller 30b to the rotating shaft 60, a conventionally known method such as via a bearing is used.

The compressor 100 is provided with a branch spray pipe 23 which is a branch flow path obtained by branching the spray pipe 22 which is a discharge flow path of the refrigerant gas flowing through the spray port 22a. The branch spray pipe 23 branches from the middle of the spray pipe 22 outside the closed container 10. At the downstream end of the branch spray pipe 23, a reverse spray port 22b is formed to blow the refrigerant onto the reverse impeller 30b so as to rotate the reverse impeller 30b in the direction of rotation 80b opposite to the direction of rotation 80c of the rotating shaft 60. ing. The branch spray pipe 23 and the reverse spray port 22b are one.

As shown in FIG. 6, the reverse spray port 22b and the spray port 22a are arranged line-symmetrically with respect to the first orthogonal line C1 orthogonal to the central axis of the rotation axis 60. The spraying directions of the refrigerant gases of the reverse spray port 22b and the spray port 22a are directed on the central axis of the rotating shaft 60 and the second orthogonal line C2 orthogonal to the first orthogonal line C1.

Here, in the second embodiment, two impellers 30a and a reverse impeller 30b are provided. However, it is not limited to this. One or more similar impellers similar to the impeller 30a and the reversing impeller 30b may be further provided.

As shown in FIG. 3, the impeller 30a is blown with the refrigerant gas from the spray port 22a and rotates in the counterclockwise rotation direction 80a when viewed from above. As shown in FIG. 6, the reversing impeller 30b is blown with refrigerant gas from the branch spray pipe 23 and rotates in the clockwise rotation direction 80b when viewed from above. As a result, the impeller 30a and the reversing impeller 30b have a so-called double reversing vane configuration, the refrigerant gas passing through the impeller 30a and the reversing impeller 30b is rectified, and the refrigerant flow path provided in the motor 7 is provided. The flow loss when passing through 7a can be suppressed. As described above, when the influence of the flow path resistance becomes less susceptible, the amount of the refrigerant gas flowing through the motor 7 increases, and as a result, the cooling effect of suppressing the heat generation of the motor 7 can be further obtained.

Further, since the flow of the refrigerant gas is rectified and the generation of a turbulent swirling flow in the closed container 10 can be suppressed, the refrigerant gas and the refrigerating machine oil can be easily separated. In addition, the separated refrigerant gas and the refrigerating machine oil can be prevented from being agitated again, and the oil rising of the refrigerating machine oil being taken out of the compressor can be reduced.

<Effect of Embodiment 2>
According to the second embodiment, the impeller 30a is rotatable with respect to the rotating shaft 60.

According to this configuration, the impeller 30a sprayed with the refrigerant from the spray port 22a rectifies the refrigerant gas sprayed, and a cooling effect can be obtained in the compressor 100.

According to the second embodiment, the rotating shaft 60 is provided with a reversing impeller 30b in the vicinity of the impeller 30a. The reversing impeller 30b is formed with a reversing spray port 22b for spraying a refrigerant so as to rotate the reversing impeller 30b in a rotation direction 80b opposite to the rotation direction 80c of the rotating shaft 60.

According to this configuration, the impeller 30a and the reversing impeller 30b form a set of so-called counter-rotating blades, and the flow of the refrigerant gas that both reciprocate and disperse can cancel each other out. Then, the twist of the flow of the blown refrigerant gas in the impeller 30a and the reversing impeller 30b is eliminated, and the effect of the blown refrigerant gas being linearly dispersed in the vertical direction and being rectified can be improved.

According to the second embodiment, there is only one reverse spray port 22b.

According to this configuration, the reversing impeller 30b is sprayed with a strong refrigerant gas from the reversing spray port 22b, and the rectifying effect of the refrigerant gas can be improved.

According to the second embodiment, the reverse spray port 22b and the spray port 22a are arranged line-symmetrically with respect to the first orthogonal line C1 orthogonal to the central axis of the rotation axis 60. The spraying directions of the refrigerant gases of the reverse spray port 22b and the spray port 22a are directed on the central axis of the rotating shaft 60 and the second orthogonal line C2 orthogonal to the first orthogonal line C1.

According to this configuration, the spraying directions of the refrigerant gases of the reverse spray port 22b and the spray port 22a are separated from each other in the compressor 100, and both refrigerant gases are sprayed vigorously separately. As a result, the impeller 30a and the reversing impeller 30b form a so-called double reversing vane set, and the flow of the refrigerant gas that both reciprocate and disperse can cancel each other more vigorously, and the impeller 30a and the reversing impeller 30b are sprayed. The twist of the flow of the refrigerant gas is eliminated, and the effect of the blown refrigerant gas being linearly dispersed in the vertical direction and being rectified can be further improved.

According to the second embodiment, the reversing impeller 30b is rotatable with respect to the rotating shaft 60.

According to this configuration, the reversing impeller 30b sprayed with the refrigerant gas from the reversing spray port 22b rectifies the refrigerant gas sprayed, and a cooling effect can be obtained in the compressor 100. Further, since the reversing impeller 30b rotates in the rotation direction 80b opposite to the rotation direction 80c of the rotating shaft 60, the reversing impeller 30b does not hinder the rotation of the rotating shaft 60.

According to the second embodiment, the reverse spray port 22b sprays the refrigerant gas of the branch spray pipe 23 as a branch flow path obtained by branching the spray pipe 22 as a discharge flow path of the refrigerant gas flowing through the spray port 22a.

According to this configuration, the reverse spray port 22b can be configured simply and inexpensively by adding the minimum number of parts.

Embodiment 3.
In the third embodiment, the description of the same items as those in the above-described embodiment will be omitted, and only the characteristic portion thereof will be described.

In the third embodiment, the impeller 30a of the second embodiment is completely fixed to the spindle 62. Refrigerant gas is blown from the spray port 22a so that the fixed impeller 30a rotates in the same rotation direction 80a as the rotation direction 80c of the spindle 62 during compressor operation. The reversing impeller 30b is rotatably attached to the spindle 62. The reversing impeller 30b is sprayed with refrigerant gas from the reversing spray port 22b so as to rotate in the rotation direction 80b opposite to that of the impeller 30a.

As a result, the compressor 100 having high performance having the characteristics of the first embodiment and the second embodiment and having reduced oil rise can be obtained.

<Effect of Embodiment 3>
According to the third embodiment, the rotating shaft 60 is provided with a reversing impeller 30b in the vicinity of the impeller 30a. The compressor 100 is formed with a reversing spray port 22b that blows a refrigerant onto the reversing impeller 30b so as to rotate the reversing impeller 30b in a rotation direction 80b opposite to the rotation direction 80c of the rotating shaft 60. The impeller 30a is fixed to the rotating shaft 60. The reversing impeller 30b is rotatable with respect to the rotating shaft 60.

According to this configuration, the impeller 30a and the reversing impeller 30b form a set of so-called double reversing blades, and the flow of the refrigerant dispersed by both can be canceled out, and the impeller 30a and the reversing impeller 30b are sprayed. The twist of the flow of the refrigerant gas is eliminated, and the effect of the blown refrigerant gas being linearly dispersed in the vertical direction and being rectified can be improved. Further, the refrigerant gas is sprayed from the spray port 22a, and the impeller 30a fixed to the rotating shaft 60 can apply an auxiliary driving force to the rotating shaft 60, so that an auxiliary effect of the driving force of the electric motor 7 can be obtained. Further, the rotatable reverse impeller 30b does not hinder the rotation of the rotating shaft 60.

Embodiment 4.
FIG. 7 is an explanatory view showing a vertical cross section of the compressor 100 according to the fourth embodiment of the present invention. In the fourth embodiment, the description of the same items as those in the above-described embodiment will be omitted, and only the characteristic portion thereof will be described.

The compressor 100 shown in FIG. 7 is a low-pressure shell type scroll compressor. In the closed container 10, the low pressure side, which is the refrigerant atmosphere before flowing into the compression mechanism portion 50, is formed in the lower space 10b. In the closed container 10, the high-pressure side, which is the refrigerant atmosphere after the refrigerant gas is compressed by the compression mechanism portion 50, is formed in the upper space 10a. The lower space 10b and the upper space 10a are separated from each other in the closed container 10 by a fixed scroll 1. The refrigerant gas in the lower space 10b is sucked into the suction chamber 14a via the suction flow path 4a formed in the fixed frame 4.

The spray port 22a formed in the inflow pipe 11 is formed at the tip of the inflow pipe 11 that flows into the lower space 10b on the low pressure side of the closed container 10 from the refrigerant circuit of the refrigeration cycle device 101. The impeller 30a is fixed to the rotating shaft 60. In the low-pressure shell type scroll compressor, the refrigerant gas compressed by the compression mechanism 50 cannot be guided to the lower space 10b, so that the tip of the inflow pipe 11 that sucks the refrigerant gas from the refrigerant circuit into the closed container 10 A spray port 22a for blowing the refrigerant gas onto the impeller 30a is formed.

<Effect of Embodiment 4>
According to the fourth embodiment, the compressor 100 is divided into a low pressure side which is a refrigerant atmosphere before flowing into the compression mechanism unit 50 and a high pressure side which is a refrigerant atmosphere after the refrigerant is compressed by the compression mechanism unit 50. The airtight container 10 is provided. The spray port 22a is formed at the tip of an inflow pipe 11 that flows into the low pressure side of the closed container 10 from the refrigerant circuit of the refrigeration cycle device 101.

According to this configuration, the refrigerant gas is blown to the impeller 30a from the spray port 22a connected to the inflow pipe 11 in the low-pressure shell type scroll compressor. Then, the refrigerant gas sprayed on the impeller 30a is rectified to obtain a cooling effect in the compressor 100. Therefore, the cooling effect can be controlled with a simple and inexpensive configuration. Further, when the spray port 22a blows the refrigerant gas onto the impeller 30a and the impeller 30a is fixed to the rotating shaft 60, an auxiliary driving force can be applied from the impeller 30a to the rotating shaft 60, and the driving force of the electric motor 7 can be applied. Auxiliary effect can be obtained.

Embodiment 5.
FIG. 8 is an explanatory view showing a vertical cross section of the compressor 100 according to the fifth embodiment of the present invention. In the fifth embodiment, the description of the same items as those in the above-described embodiment will be omitted, and only the characteristic portion thereof will be described.

As shown in FIG. 8, the compressor 100 is a low-pressure shell type scroll compressor. The reversing spray port 22b for blowing the refrigerant gas onto the reversing impeller 30b is formed at the tip of the branch inflow pipe 13 which is a branch flow path in which the inflow pipe 11 of the refrigerant flowing through the spray port 22a is branched.

The impeller 30a may be fixed to the rotating shaft 60 or may be rotatable with respect to the rotating shaft 60. Further, the reversing impeller 30b is rotatable with respect to the rotating shaft 60.

<Effect of Embodiment 5>
According to the fifth embodiment, the reverse spray port 22b sprays the refrigerant gas of the branch inflow pipe 13 as a branch flow path obtained by branching the inflow pipe 11 of the refrigerant gas flowing through the spray port 22a.

According to this configuration, the reverse spray port 22b can be configured simply and inexpensively by adding the minimum number of parts.

In addition, embodiments 1 to 5 of the present invention may be combined, or may be applied to other parts. Here, a high-pressure shell type and a low-pressure shell type scroll compressor are taken as an example. However, it is not limited to this. For example, the compressor 100 having the electric motor 7 in the closed container 10 and the rotating shaft 60 to which the impeller 30a can be attached is not limited to the scroll compressor.

Embodiment 6.
<Refrigeration cycle device 101>
FIG. 9 is a refrigerant circuit diagram showing a refrigeration cycle device 101 to which the compressor 100 according to the sixth embodiment of the present invention is applied.

As shown in FIG. 9, the refrigeration cycle device 101 includes a compressor 100, a condenser 102, an expansion valve 103, and an evaporator 104. The compressor 100, the condenser 102, the expansion valve 103, and the evaporator 104 are connected by a refrigerant pipe to form a refrigeration cycle circuit. Then, the refrigerant flowing out of the evaporator 104 is sucked into the compressor 100 and becomes high temperature and high pressure. The high temperature and high pressure refrigerant is condensed in the condenser 102 to become a liquid. The liquid refrigerant is decompressed and expanded by the expansion valve 103 to become a low-temperature low-pressure gas-liquid two-phase, and the gas-liquid two-phase refrigerant is heat-exchanged in the evaporator 104.

The compressor 100 of the first to fifth embodiments can be applied to such a refrigeration cycle device 101. Examples of the refrigeration cycle device 101 include an air conditioner, a refrigeration device, a water heater, and the like.

<Effect of Embodiment 6>
According to the sixth embodiment, the refrigeration cycle device 101 includes the compressor 100 described above.

According to this configuration, in the refrigeration cycle device 101 provided with the compressor 100, the cooling effect can be controlled with a simple and inexpensive configuration.

1 Fixed scroll, 1a base plate part, 1b plate-shaped spiral tooth, 1c oldham guide groove, 2 swing scroll, 2a base plate part, 2b plate-shaped spiral tooth, 2c boss part, 2d swing bearing, 2e thrust surface, 2f Oldham guide groove, 3 movable frame, 3a thrust receiver, 3b sliding surface, 3c main bearing, 4 fixed frame, 4a suction flow path, 5 oldam mechanism, 5a fixed side key, 5b swing side key, 5c annular part, 7 Motor, 7a refrigerant flow path, 10 closed container, 10a upper space, 10b lower space, 11 inflow pipe, 12 discharge pipe, 13 branch inflow pipe, 14a suction chamber, 14b compression chamber, 14c innermost chamber, 16 volt, 21 partition Plate, 22 spray pipe, 22a spray port, 22b reverse spray port, 22c discharge flow path, 23 branch spray pipe, 30a impeller, 30b reverse impeller, 50 compression mechanism, 60 rotation shaft, 61 swing shaft, 62 spindle , 63 Refueling pump, 70 Oil reservoir, 80a rotation direction, 80b rotation direction, 80c rotation direction, 100 compressor, 101 refrigeration cycle device, 102 condenser, 103 expansion valve, 104 evaporator.

Claims (16)

A compression mechanism that compresses and discharges the refrigerant,
A rotating shaft that rotates to transmit power to the compression mechanism,
An electric motor that rotationally drives the rotating shaft and
An impeller provided on the rotating shaft and
The flow path through which the refrigerant flows and
With
A compressor in which a spray port for spraying the refrigerant on the impeller is formed in the flow path. The axis of rotation extends axially along the vertical direction.
An oil reservoir is formed around the lower end of the rotating shaft.
The compression mechanism portion is provided on the upper end side of the rotating shaft.
The electric motor is provided below the compression mechanism portion, and is provided.
The compressor according to claim 1, wherein the impeller is provided between the motor and the oil reservoir. The compressor according to claim 1 or 2, wherein the spray port sprays the refrigerant so as to rotate the impeller in the same direction as the rotation direction of the rotation shaft. The compressor according to any one of claims 1 to 3, wherein the spray port is one. The compressor according to any one of claims 1 to 4, wherein the impeller is fixed to the rotating shaft. The compressor according to any one of claims 1 to 4, wherein the impeller is rotatable with respect to the rotating shaft. A reversing impeller is provided on the rotating shaft in the vicinity of the impeller.
The one according to any one of claims 1 to 6, wherein a reversing impeller is formed with a reversing spray port for spraying the refrigerant so as to rotate the reversing impeller in a direction opposite to the rotation direction of the rotating shaft. Compressor. The compressor according to claim 7, wherein the reverse spray port is one. The reverse spray port and the spray port are arranged line-symmetrically with respect to a first orthogonal line orthogonal to the central axis of the rotation axis.
The compressor according to claim 8, wherein the direction of spraying the refrigerant between the reverse spray port and the spray port is directed on the central axis of the rotation axis and the second orthogonal line orthogonal to the first orthogonal line. The compressor according to any one of claims 7 to 9, wherein the reversing impeller is rotatable with respect to the rotating shaft. The compressor according to any one of claims 1 to 10, wherein the spray port is formed at the tip of a discharge flow path through which the refrigerant discharged from the compression mechanism section is circulated. The reverse spray port is any one of claims 8 to 11, which is dependent on claim 7 or claim 7, in which the refrigerant of the branch flow path branched from the discharge flow path of the refrigerant flowing through the spray port is sprayed. The compressor according to item 1. A closed container is provided in which the high-pressure side, which is the atmosphere of the refrigerant after the refrigerant is compressed by the compression mechanism, is divided into two.
The discharge flow path is a spray pipe that allows the refrigerant once discharged from the first high-pressure side of the closed container to flow out of the closed container to the second high-pressure side of the closed container. The compressor according to claim 11 or 12. A closed container is provided which is divided into a low pressure side which is a refrigerant atmosphere before flowing into the compression mechanism portion and a high pressure side which is a refrigerant atmosphere after the refrigerant is compressed by the compression mechanism portion.
The compressor according to any one of claims 1 to 10, wherein the spray port is formed at the tip of an inflow pipe that flows from the refrigerant circuit of the refrigeration cycle device to the low pressure side of the closed container. The compressor according to claim 6, wherein the reverse spray port is dependent on claim 6 or 7, in which the refrigerant of the branch flow path branched from the inflow pipe of the refrigerant flowing through the spray port is sprayed. A refrigeration cycle apparatus comprising the compressor according to any one of claims 1 to 15.

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