JPWO2019111461A1 - Twin rotary compressor and refrigeration cycle device - Google Patents

Abstract

The twin rotary compressor includes an electric motor, a crankshaft, a piston, a cylinder, and an injection flow path for injecting a refrigerant into a compression chamber from an external refrigerant pipe. The injection flow path includes a first injection port, A second injection port, an injection inlet pipe, a first injection pipe, a second injection pipe, and an injection muffler, wherein the first injection pipe and the second injection pipe are separately connected to the injection muffler. It

Description

The present invention relates to a twin rotary compressor and a refrigeration cycle device having an injection flow path.

Conventionally, a rotary compressor is equipped with an electric motor composed of a rotor and a stator in an upper part of a closed container. Then, the rotation of the electric motor is transmitted to the eccentric portion provided in the lower portion by the crankshaft fixed to the rotor. A piston is provided in the eccentric portion, and the crankshaft rotates to eccentrically move the piston to reduce the volume of the compression chamber. Thereby, in the rotary compressor, the refrigerant is compressed in the compression chamber.

In addition, an injection port may be formed in the compression chamber. In this case, the intermediate pressure liquid or gas refrigerant is injected into the compression chamber from the injection flow path connected to the injection port.

Here, a technique having an injection muffler in the injection flow path is known (for example, refer to Patent Document 1). It is said that the injection muffler can absorb the pressure fluctuation generated in the compression chamber and the pressure pulsation of the injection refrigerant, and can stably and smoothly supply the refrigerant to be injected.

Japanese Utility Model Publication No. 1-58046

By the way, in the case of the rotary compressor to which the injection muffler is applied, not only the pressure fluctuation and the pressure pulsation of the injection refrigerant that occur in the compression chamber can be absorbed but also a supercharging effect of increasing the flow rate of the injection refrigerant can be exhibited. Was found. In particular, it has been found that the twin rotary compressor can obtain a supercharging effect for each of the two compression chambers.

The present invention is for solving the above-mentioned problems, and is capable of absorbing the pressure fluctuation and the pressure pulsation of the injection refrigerant that occur in the compression chamber, and is a highly efficient twin that can exhibit the supercharging effect of increasing the flow rate of the injection refrigerant. An object is to provide a rotary compressor and a refrigeration cycle device.

A twin rotary compressor according to the present invention includes an electric motor having a stator and a rotor, a first eccentric portion provided on a main shaft fixed to the rotor, and a second eccentric portion provided on the main shaft. A crankshaft rotated by the electric motor, a first piston provided in the first eccentric portion, a second piston provided in the second eccentric portion, and a cylindrical through hole. A first cylinder having a first compression chamber formed by arranging the first eccentric portion and the first piston in the through hole; and a cylindrical through hole formed in the through hole. A rotary compressor including a second cylinder in which a second compression chamber is formed by arranging a second eccentric portion and the second piston, wherein the first compression chamber and the An injection flow path for injecting a refrigerant into each of the second compression chambers is provided, and the injection flow path includes a first injection port formed in the first compression chamber and a second injection port formed in the second compression chamber. A port, an injection inlet pipe connected to the refrigerant pipe, a first injection pipe for supplying a refrigerant to the first injection port, a second injection pipe for supplying a refrigerant to the second injection port, and the injection inlet A pipe and an injection muffler arranged between the first injection pipe and the second injection pipe and having a diameter larger than the inner diameters of the first injection pipe and the second injection pipe. The injection pipe and the second injection pipe are separately connected to the injection muffler.

A refrigeration cycle apparatus according to the present invention includes the above twin rotary compressor.

According to the twin rotary compressor and the refrigeration cycle device of the present invention, the twin rotary compressor and the refrigeration cycle device are arranged between the injection inlet pipe and the first injection pipe and the second injection pipe, and are wider than the inner diameters of the first injection pipe and the second injection pipe. The injection muffler has a diameter, and the first injection pipe and the second injection pipe are separately connected to the injection muffler. Therefore, the pressure fluctuation and the pressure pulsation of the injection refrigerant generated in the compression chamber can be absorbed, and the supercharging effect of increasing the flow rate of the injection refrigerant can be exhibited. Therefore, the twin rotary compressor becomes highly efficient.

It is a refrigerant circuit diagram showing a refrigerating cycle device to which a twin rotary compressor concerning Embodiment 1 of the present invention is applied. It is a longitudinal section showing a twin rotary compressor concerning Embodiment 1 of the present invention. It is a cross-sectional view showing the injection port in the compression chamber according to the first embodiment of the present invention. It is a figure which shows the relationship between the supercharging rate (alpha) exceeding 100% and the length L of the injection pipe, and the inner diameter d which concerns on Embodiment 1 of this invention. It is a figure which shows the relationship between the supercharging rate (alpha) which concerns on Embodiment 1 of this invention, the length L, and the inner diameter d of an injection pipe. FIG. 7 is a vertical cross-sectional view showing a twin rotary compressor according to Modification 1 of Embodiment 1 of the present invention. FIG. 9 is a vertical cross-sectional view showing a twin rotary compressor according to Modification 2 of Embodiment 1 of the present invention. FIG. 6 is a vertical cross-sectional view showing a twin rotary compressor according to Modification 3 of Embodiment 1 of the present invention. FIG. 9 is a vertical cross-sectional view showing a twin rotary compressor according to Modification 4 of Embodiment 1 of the present invention. FIG. 9 is a vertical cross-sectional view showing a twin rotary compressor according to Modification 5 of Embodiment 1 of the present invention. FIG. 11 is a vertical cross-sectional view showing a twin rotary compressor according to Modification 6 of Embodiment 1 of the present invention. FIG. 11 is a vertical cross-sectional view showing a twin rotary compressor according to Modification 7 of Embodiment 1 of the present invention. FIG. 10 is a vertical cross-sectional view showing a twin rotary compressor according to Modification 8 of Embodiment 1 of the present invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, in each of the drawings, the same reference numerals are the same or equivalent, and this is common to all the texts of the specification. Further, in the drawings of the cross-sectional views, hatching is appropriately omitted in view of visibility. Further, the forms of the constituent elements shown in the entire specification are merely examples, and the present invention is not limited to these descriptions.

Embodiment 1.
<Refrigeration cycle device 200>
1 is a refrigerant circuit diagram showing a refrigeration cycle apparatus 200 to which a twin rotary compressor 100 according to Embodiment 1 of the present invention is applied.

As shown in FIG. 1, the refrigeration cycle device 200 includes a twin rotary compressor 100, a condenser 201, an expansion valve 202, and an evaporator 203. The twin rotary compressor 100, the condenser 201, the expansion valve 202 and the evaporator 203 are connected by a refrigerant pipe 204 to form a refrigeration cycle circuit. Then, the refrigerant flowing out of the evaporator 203 is sucked into the twin rotary compressor 100 and becomes high temperature and high pressure. The high-temperature and high-pressure refrigerant is condensed in the condenser 201 to become a liquid. The liquid refrigerant is decompressed and expanded by the expansion valve 202 to become a low temperature and low pressure gas-liquid two-phase, and the gas-liquid two-phase refrigerant is heat-exchanged in the evaporator 203.

The refrigeration cycle apparatus 200 includes an injection flow path 205 for injecting the refrigerant into the compression chamber from the refrigerant pipe 204 before the evaporator 203 and further before the expansion valve 202 in the refrigerant circulation direction of the refrigeration cycle circuit. Details of the injection flow channel 205 will be described later.

The twin rotary compressor 100 described below can be applied to such a refrigeration cycle apparatus 200. Examples of the refrigeration cycle device 200 include an air conditioner, a refrigeration device, a water heater, and the like.

<Structure of twin rotary compressor 100>
FIG. 2 is a vertical sectional view showing the twin rotary compressor 100 according to Embodiment 1 of the present invention. FIG. 3 is a cross-sectional view showing the injection port in the compression chamber according to the first embodiment of the present invention.

As shown in FIG. 2, the twin rotary compressor 100 includes a tubular closed container 101 whose upper and lower ends are closed. The closed container 101 has a tubular member 101a, a bowl-shaped upper end closing member 101b that closes the upper end of the tubular member 101a, and a bowl-shaped lower end closing member 101c that closes the lower end of the tubular member 101a. The closed container 101 is installed and fixed to the pedestal 102.

An electric motor 103 is arranged in the upper part of the closed container 101. The electric motor 103 has a stator 103a and a rotor 103b. The stator 103 a of the electric motor 103 has a cylindrical shape and is fixed to the inner peripheral wall portion of the closed container 101. The rotor 103b has a columnar shape, and is arranged in a hollow portion formed in the center of the stator 103a so as to be rotatable in the horizontal direction and the circumferential direction.

A crankshaft 104, which is rotated by an electric motor 103, is arranged in the closed casing 101 so as to extend in the vertical direction. The crankshaft 104 has a main shaft 104a, a first eccentric portion 104b, a second eccentric portion 104c, and a sub shaft 104d.

The main shaft 104a is fixed to the rotor 103b. The main shaft 104a transmits the rotational driving force from the rotor 103b to the first eccentric portion 104b and the second eccentric portion 104c. The first eccentric part 104b is provided on the main shaft 104a on the main shaft 104a side above the second eccentric part 104c, eccentric to the main shaft 104a and the center line, and has a larger diameter than the main shaft 104a. The second eccentric portion 104c is provided on the main shaft 104a on the side of the sub shaft 104d below the first eccentric portion 104b, eccentric to the main shaft 104a and the first eccentric portion 104b, and has a diameter larger than that of the main shaft 104a. Is big.

As shown in FIG. 3, the first eccentric portion 104b is provided with a first piston 105a. The first piston 105a has a partition member 105a1 that partitions the first compression chamber 106a.

The 1st eccentric part 104b and the 1st piston 105a are arrange|positioned in the 1st cylinder 107a in which the cylindrical through-hole was formed. The first eccentric portion 104b and the first piston 105a are arranged in the through hole of the first cylinder 107a to form the first compression chamber 106a. The first compression chamber 106a is a closed cylindrical space. A first inflow refrigerant pipe 108a is connected to the first cylinder 107a via a through hole 107a1.

Further, as in FIG. 3, the second eccentric portion 104c is provided with a second piston (not shown). The second piston has a partition member that partitions the second compression chamber.

The second eccentric portion 104c and the second piston are arranged below the first cylinder 107a in the second cylinder 107b in which a cylindrical through hole is formed. A second compression chamber is formed by disposing the second eccentric portion 104c and the second piston in the through hole of the second cylinder 107b. The second compression chamber is a closed cylindrical space. The second inflow refrigerant pipe 108b is connected to the second cylinder 107b via a through hole.

An upper bearing 109a, which constitutes the upper wall of the first compression chamber 106a, is provided on the upper end of the first cylinder 107a while slidably holding the crankshaft 104.

At the lower end of the second cylinder 107b, a lower bearing 109b that constitutes a lower wall portion of the second compression chamber is provided while slidably holding the crankshaft 104.

A lower wall portion of the first compression chamber 106a and an upper wall portion of the second compression chamber 106a are formed between the first cylinder 107a and the second cylinder 107b, and partition the first compression chamber 106a and the second compression chamber. An intermediate plate 110 is provided.

An upper discharge muffler 111a that covers the upper bearing 109a is provided above the upper bearing 109a. The upper discharge muffler 111a surrounds the compressed refrigerant discharge port 107a2 of the first cylinder 107a. Below the lower bearing 109b, a lower discharge muffler 111b that covers the lower bearing 109b is provided. The lower discharge muffler 111b surrounds the outlet of the compressed refrigerant of the second cylinder 107b. The upper discharge muffler 111a and the lower discharge muffler 111b reduce noise amplified by resonance of the internal space in the closed container 101. The compressed refrigerant discharged from the upper discharge muffler 111a and the lower discharge muffler 111b is supplied to the refrigerant pipe 204 of the refrigeration cycle circuit from the discharge pipe 112 provided at the upper part of the closed container 101.

Both of the first inflow refrigerant pipe 108a and the second inflow refrigerant pipe 108b are inserted into the suction muffler 113. The suction muffler 113 is connected to the refrigerant pipe 204 of the refrigeration cycle circuit and allows the refrigerant to flow therein. The suction muffler 113 is fixed to the outer circumference of the closed container 101.

<Operation of the twin rotary compressor 100>
Refrigerating machine oil is accumulated at the bottom of the closed container 101. The refrigerating machine oil collected at the bottom is sucked up by the rotation of the crankshaft 104 from a hollow hole provided in the crankshaft 104 in the manner of a centrifugal pump utilizing the rotation of the crankshaft 104. The sucked up refrigerating machine oil is circulated to each sliding portion through the oil supply hole opened from the hollow hole of the crankshaft 104 toward the outer peripheral portion. Thereby, the mechanical part is sealed by the refrigerating machine oil. Therefore, the crankshaft 104, the first piston 105a, the second piston, the first cylinder 107a, the second cylinder 107b, the upper bearing 109a, the lower bearing 109b, and the intermediate plate 110, which are sliding parts, do not come into direct contact with each other, Damage is prevented and further refrigerant leakage is prevented.

An oil separator (not shown) is fitted on the crankshaft 104. The oil separator prevents the refrigeration oil together with the discharged refrigerant from flowing out of the discharge pipe 112. The oil separator closes the flow path for the mixed fluid of the refrigerant and the refrigerating machine oil flowing toward the discharge pipe 112, collides and separates the refrigerant and the refrigerating machine oil, and suppresses the outflow of the refrigerating machine oil to the outside of the machine.

In the twin rotary compressor 100, the crankshaft 104 fixed to the rotor 103b of the motor section is rotated by the electric motor 103. Thereby, the 1st eccentric part 104b and the 2nd eccentric part 104c, and the 1st piston 105a and the 2nd piston which were respectively attached to the outer peripheral part of the 1st eccentric part 104b and the 2nd eccentric part 104c, Eccentric rotation. Then, the volumes of the first compression chamber 106a and the second compression chamber are reduced, the refrigerant is compressed, and the pressure is changed to high pressure.

<Details of injection flow path 205>
As shown in FIG. 1, the injection flow path 205 includes a refrigerant pipe 204 in front of the evaporator 203 and further in front of the expansion valve 202 from the refrigerant pipe 204 in the refrigerant circulation direction of the refrigeration cycle circuit to the first compression chamber 106a and the second compression chamber, respectively. Inject the refrigerant into.

The injection flow path 205 includes a first injection port 205a1, a second injection port 205a2, an injection inlet pipe 205b, a first injection pipe 205c, a second injection pipe 205d, an injection muffler 205e, and a first in-machine passage 205f1. And a second in-machine passage 205f2.

As shown in FIGS. 2 and 3, the first injection port 205a1 is formed in the first compression chamber 106a by opening a part of the upper bearing 109a. The second injection port 205a2 is formed in the second compression chamber by opening a part of the lower bearing 109b.

As shown in FIG. 2, the injection inlet pipe 205b forming the injection flow passage 205 is connected to the refrigerant pipe 204 of the refrigeration cycle circuit and also to the injection muffler 205e. The injection inlet pipe 205b is separated from the first injection pipe 205c and the second injection pipe 205d protruding upward in the injection muffler 205e at the upper part of the injection muffler 205e, and projects downward in the injection muffler 205e.

The first injection pipe 205c has an inflow port inserted into the injection muffler 205e, is connected to the first in-machine passage 205f1, and supplies the refrigerant to the first injection port 205a1. The second injection pipe 205d has an inflow port inserted into the injection muffler 205e, is connected to the second in-machine passage 205f2, and supplies the refrigerant to the second injection port 205a2. The first injection pipe 205c and the second injection pipe 205d are separately connected to the injection muffler 205e. The second injection pipe 205d is longer than the first injection pipe 205c because the second injection pipe 205d is connected to the lower portion of the closed container 101 more than the first injection pipe 205c.

The injection muffler 205e is arranged between the injection inlet pipe 205b, the first injection pipe 205c, and the second injection pipe 205d. The inner diameter of the injection muffler 205e is larger than the inner diameters of the first injection pipe 205c and the second injection pipe 205d. As a result, the first injection pipe 205c and the second injection pipe 205d are inserted at two locations in the circular bottom portion of the injection muffler 205e.

The first injection pipe 205c and the second injection pipe 205d project upward into the injection muffler 205e at the lower part of the injection muffler 205e. The protrusion amount B[m] of the first injection pipe 205c and the second injection pipe 205d protruding in the injection muffler 205e is 10% or less of the vertical length A[m] in the injection muffler 205e. As a result, the first injection pipe 205c and the second injection pipe 205d have appropriate lengths that allow injection of both the gas refrigerant and the liquid refrigerant, and project in the injection muffler 205e.

The injection muffler 205e is fixed to the outer peripheral portion of the closed container 101 similarly to the suction muffler 113. The volume of the injection muffler 205e is 5% or more of the volume of the suction muffler 113. The volume of the injection muffler 205e is based on the relationship between the suction refrigerant and the injection refrigerant.

The first in-machine passage 205f1 connects the first injection pipe 205c and the first injection port 205a1. The first in-machine passage 205f1 is formed as a through hole or the like inside the upper bearing 109a. The second in-machine passage 205f2 connects the second injection pipe 205d and the second injection port 205a2. The second in-machine passage 205f2 is formed as a through hole or the like inside the lower bearing 109b.

<Operation of Injection Flow Path 205>
The refrigerant flowing from the refrigeration cycle circuit through the injection flow passage 205 flows into the injection muffler 205e through the injection inlet pipe 205b. The refrigerant flowing into the injection muffler 205e is supplied to the first injection pipe 205c and the second injection pipe 205d in the injection muffler 205e. The refrigerant supplied to the first injection pipe 205c is injected as a liquid or gas refrigerant from the first injection port 205a1 into the first compression chamber 106a through the first in-machine passage 205f1 of the twin rotary compressor 100. The refrigerant supplied to the second injection pipe 205d is injected as a liquid or gas refrigerant from the second injection port 205a2 into the inside of the second compression chamber through the second in-machine passage 205f2 of the twin rotary compressor 100.

At this time, the pressure in the injection muffler 205e includes the injection pressure from the refrigeration cycle circuit and the pressures of the first injection pipe 205c and the second injection pipe 205d supplied to the first compression chamber 106a and the second compression chamber. Intermediate pressure. Therefore, the refrigerant is unlikely to leak due to the pressure difference between the first compression chamber 106a and the second compression chamber.

The pressures of the first injection pipe 205c and the second injection pipe 205d fluctuate depending on the phases of the first piston 105a and the second piston. However, the first injection pipe 205c and the second injection pipe 205d are connected to the injection inlet pipe 205b via the injection muffler 205e that keeps the internal pressure at an intermediate pressure. Therefore, since the pressure of the injection inlet pipe 205b is kept constant, the refrigerant injected from the injection flow passage 205 is stable and the loss is small.

<Characteristics of injection channel 205>
In addition to the above, the shape of the injection muffler 205e or the length and inner diameter of the first injection pipe 205c and the second injection pipe 205d are designated and designed. As a result, a supercharging effect is obtained when the injection refrigerant is sucked. As a result, the flow rate of the injection refrigerant increases, and the injection refrigerant can be injected with high efficiency.

Here, the inventors have obtained the following findings. That is, the supercharging of the injection refrigerant is caused by the pressure fluctuations at the inlet and the outlet of the first injection pipe 205c and the second injection pipe 205d that suck the refrigerant being overlapped and amplified. The reason why the pressure fluctuations at the inlet and the outlet of the first injection pipe 205c and the second injection pipe 205d differ from each other is that the refrigerant is generated when the refrigerant passes through the injection muffler 205e, the first injection pipe 205c, or the second injection pipe 205d. Due to friction loss. Therefore, the supercharging rate has a correlation with the equation of pressure loss due to pipe friction loss.

The pipe friction coefficient of the first injection pipe 205c or the second injection pipe 205d is defined as λ. The length of each of the first injection pipe 205c and the second injection pipe 205d is defined as L[m]. Here, the length L is the length between the tip of the first injection pipe 205c or the second injection pipe 205d exposed to the outside from the injection muffler 205e and the tip exposed to the outside from the closed container 101. The first injection pipe 205c or the second injection pipe 205d is actually inserted in the injection muffler 205e and the closed container 101, but the length L here is the length on the center line of the portion exposed to the outside. is there. The inner diameter of each of the first injection pipe 205c or the second injection pipe 205d is defined as d[m]. The flow velocity of the refrigerant flowing through each of the first injection pipe 205c and the second injection pipe 205d is defined as v [m/s]. The density of the refrigerant flowing through each of the first injection pipe 205c and the second injection pipe 205d is defined as ρ [kg/m]. At this time, the pressure loss ΔP [Pa] at the outlet of each of the first injection pipe 205c or the second injection pipe 205d is
ΔP=λ×(L/d)×1/2×ρ×v ² .

Here, the flow rate of the refrigerant flowing through each of the first injection pipe 205c and the second injection pipe 205d is defined as Q [m ³ /s]. The cross-sectional area of each of the first injection pipe 205c and the second injection pipe 205d is defined as (d/2) ² ×π. In that case, since the refrigerant flow rate v=Q/((d/2) ² ×π), v in the equation of ΔP is replaced, and ΔP is
ΔP=(L/d ⁵ )×(8/π ² ×λ×ρ×Q ² ).

Further, when (8/π ² ×λ×ρ×Q ² ) is replaced with a coefficient J [kg·m ³ /s ² ] having a correlation with λ, ρ, and Q, ΔP becomes
ΔP=J×(L/d ⁵ ).

Here, ΔP is divided by the pressure loss Pbase [Pa] when there is no supercharging effect in each of the first injection pipe 205c or the second injection pipe 205d, multiplied by 100, and the first injection pipe 205c or When the supercharging rate α [%] having a supercharging effect is calculated in each of the second injection pipes 205d, α is
α=ΔP/Pbase×100=J×100/Pbase×(L/d ⁵ ).
The supercharging rate α is calculated as an increasing rate that exceeds 100%, which is larger than the case where there is no supercharging effect is less than 100%.

When J×100/Pbase is replaced with a coefficient K [kg·m ³ /(s ² ·Pa)] having a correlation with λ, ρ, Q, and Pbase,
α=K×(L/d ⁵ )... (Equation 1)

FIG. 4 is a diagram showing a relationship between the supercharging rate α exceeding 100% and the length L and the inner diameter d of the first injection pipe 205c and the second injection pipe 205d according to the first embodiment of the present invention. As shown in FIG. 4, it is designed to include a first injection pipe 205c and a second injection pipe 205d that have a combination of L and d in which the supercharging rate α exceeds 100% while the supercharging rate α changes. To be done.

Then, α, L, and d have a correlation using the coefficient K. As a result, the length L and the inner diameter d of the first and second injection pipes 205c and 205d can be designed by using the following relational expressions (Equation 2) and (Equation 3).
L=(α×d ⁵ )/K (Equation 2)
d=(K×L/α) ^1/5 (Equation 3)

FIG. 5 is a diagram showing a relationship between the supercharging rate α and the length L and the inner diameter d of the first and second injection pipes 205c and 205d according to the first embodiment of the present invention. From FIG. 5, in order to further obtain the supercharging effect, it is more preferable that the length L and the inner diameter d of the first and second injection pipes 205c and 205d satisfy the following relationships.
When the maximum value of α obtained by the combination of L and d is αmax, the first injection pipe 205c having a combination of L and d that obtains α in the range of (αmax+1)/2≦α≦αmax, It is designed to include the second injection pipe 205d.
Then, L is in the range of (αmax+1)/2≦α≦αmax while satisfying the above relational expression (Expression 2) obtained by modifying (Expression 1).
d is a range of (αmax+1)/2≦α≦αmax while satisfying the above (Formula 3) obtained by modifying (Formula 1).

<Example>
The length L of the first injection pipe 205c is L=0.169 [m]. The length L of the second injection pipe 205d is L=0.221 [m]. The inner diameter d of the first and second injection pipes 205c and 205d is d=0.004 [m]. The volume of the injection muffler 205e is 0.00073 [m ³ ]. The volume of the suction muffler 113 is 0.00731 [m ³ ]. In such a case, the following is obtained from the above relational expression (Equation 1) and various configurations.

That is, the supercharging rate α in the first injection pipe 205c is α=122.7%. The supercharging rate α in the second injection pipe 205d is α=123.7%. As described above, the conditions for exerting the supercharging effect are satisfied. Further, the volume of the injection muffler 205e is 10% of the volume of the suction muffler 113, which satisfies the condition necessary for the relationship between the suction refrigerant and the injection refrigerant. As described above, in this case, the pressure fluctuation generated in the first compression chamber 106a and the second compression chamber and the pressure pulsation of the injection refrigerant can be absorbed, and the supercharging effect of increasing the flow rate of the injection refrigerant can be exhibited. Therefore, the twin rotary compressor 100 becomes highly efficient.

<Modification 1>
FIG. 6 is a vertical cross-sectional view showing a twin rotary compressor 100 according to Modification 1 of Embodiment 1 of the present invention. In the first modification, description of the same matters as in the above-described embodiment will be omitted, and only the characteristic parts thereof will be described.

As shown in FIG. 6, in the twin rotary compressor 100, the connection points of the outlets of the first injection pipe 205c and the second injection pipe 205d are different from those in the above-described embodiment. That is, the outlet of the first injection pipe 205c is connected to the passage in the intermediate plate 110. The outlet of the second injection pipe 205d is connected to the passage of the lower bearing 109b.

<Modification 2>
FIG. 7 is a vertical cross-sectional view showing a twin rotary compressor 100 according to Modification 2 of Embodiment 1 of the present invention. In the second modification, description of items similar to those of the above-described embodiment will be omitted, and only the characteristic parts thereof will be described.

As shown in FIG. 7, in the twin rotary compressor 100, the connection points of the outlets of the first injection pipe 205c and the second injection pipe 205d are different from those in the above-described embodiment. That is, the outlet of the first injection pipe 205c is connected to the passage of the upper bearing 109a. The outlet of the second injection pipe 205d is connected to the passage in the intermediate plate 110.

<Modification 3>
FIG. 8 is a vertical cross-sectional view showing a twin rotary compressor 100 according to Modification 3 of Embodiment 1 of the present invention. In the modified example 3, the description of the same matters as those in the above-described embodiment is omitted, and only the characteristic part will be described.

As shown in FIG. 8, in the twin rotary compressor 100, the connection points of the outlets of the first injection pipe 205c and the second injection pipe 205d are different from those in the above-described embodiment. That is, the outlets of the first injection pipe 205c or the second injection pipe 205d are connected to either the first cylinder 107a or the second cylinder 107b with their positions in the circumferential direction displaced, and the upper bearing 109a or the lower bearing is inserted from the inside thereof. It is connected to the passage in 109b and the passage in the intermediate plate 110, respectively.

<Modification 4>
FIG. 9 is a vertical cross-sectional view showing a twin rotary compressor 100 according to Modification 4 of Embodiment 1 of the present invention. In the modified example 4, description of matters similar to those of the above-described embodiment will be omitted, and only the characteristic portions thereof will be described.

As shown in FIG. 9, in the twin rotary compressor 100, the connection points of the outlets of the first injection pipe 205c and the second injection pipe 205d are different from those in the above-described embodiment. That is, the outlet of the first injection pipe 205c is connected to the first cylinder 107a, and the inside thereof is connected to the passage in the upper bearing 109a. The outlet of the second injection pipe 205d is connected to the second cylinder 107b, and is connected to the passage in the lower bearing 109b from the inside.

<Modification 5>
FIG. 10 is a vertical cross-sectional view showing a twin rotary compressor 100 according to Modification 5 of Embodiment 1 of the present invention. In the modified example 5, the description of the same matters as those in the above-described embodiment is omitted, and only the characteristic part will be described.

As shown in FIG. 10, in the twin rotary compressor 100, the inner diameters D1[m] and D2[m] of the first injection pipe 205c and the second injection pipe 205d are different from each other. That is, the inner diameter D1 of the first injection pipe 205c in which the length L1[m] of the pipe is shorter than the length L2[m] of the second injection pipe 205d is smaller than the inner diameter D2 of the second injection pipe 205d. That is, the inner diameters D1 and D2 of the first injection pipe 205c and the second injection pipe 205d are preferably smaller as the lengths of the first injection pipe 205c and the second injection pipe 205d are shorter.

<Modification 6>
FIG. 11 is a vertical cross-sectional view showing a twin rotary compressor 100 according to Modification 6 in Embodiment 1 of the present invention. In the modified example 6, description of items similar to those of the above-described embodiment will be omitted, and only the characteristic parts thereof will be described.

As shown in FIG. 11, in the twin rotary compressor 100, at least one of the first injection pipe 205c and the second injection pipe 205d is connected to the first injection port 205a1 or the second injection port 205a2 at an inner diameter D3[ A connection pipe 206 in which m] is smaller than the inner diameter D of the first injection pipe 205c or the second injection pipe 205d is provided. That is, the inner diameter D3 is the inner diameter D of the first injection pipe 205c and the second injection pipe 205d at the connection portion of the first injection pipe 205c, which has a shorter pipe length than the second injection pipe 205d, with the first injection port 205a1. A smaller connecting tube 206 is provided.

<Modification 7>
FIG. 12 is a vertical cross-sectional view showing a twin rotary compressor 100 according to Modification 7 of Embodiment 1 of the present invention. In the modified example 7, description of the same matters as those in the above-described embodiment is omitted, and only the characteristic part will be described. Modification 7 is a combination of Modifications 5 and 6.

As shown in FIG. 12, in the twin rotary compressor 100, the inner diameters D1 and D2 of the first injection pipe 205c and the second injection pipe 205d are different from each other. In addition, at least one of the first injection pipe 205c and the second injection pipe 205d is connected to the first injection port 205a1 or the second injection port 205a2 at the connection portion with the inner diameter D3 of the first injection pipe 205c or the second injection pipe 205d. A connecting pipe 206 smaller than the inner diameters D1 and D2 of is provided. That is, the inner diameter D1 of the first injection pipe 205c in which the length L1 of the pipe is shorter than the length L2 of the second injection pipe 205d is smaller than the inner diameter D2 of the second injection pipe 205d. In addition, the inner diameter D3 of the first injection pipe 205c and the second injection pipe 205d is smaller than that of the first injection pipe 205c, which has a shorter pipe length L1 than the second injection pipe 205d, and is connected to the first injection port 205a1. A connecting pipe 206 smaller than the inner diameters D1 and D2 is provided.

<Modification 8>
FIG. 13 is a vertical cross-sectional view showing a twin rotary compressor 100 according to Modification Example 8 of Embodiment 1 of the present invention. In the modified example 8, description of the same matters as those in the above-described embodiment is omitted, and only the characteristic part will be described.

As shown in FIG. 13, in the twin rotary compressor 100, the projecting amounts B1[m] and B2[m] protruding in the respective injection mufflers 205e of the first injection pipe 205c and the second injection pipe 205d are the same as each other. different. That is, the protrusion amount B1 that projects in the injection muffler 205e of the first injection pipe 205c in which the length L1 of the pipe is shorter than the length L2 of the second injection pipe 205d is the amount of protrusion in the injection muffler 205e of the second injection pipe 205d. Is longer than the protruding amount B2. That is, the protruding amount B1 or B2 protruding in the injection muffler 205e of each of the first injection pipe 205c and the second injection pipe 205d is longer as the length of the first injection pipe 205c and the second injection pipe 205d is shorter. good.

<Effect of Embodiment 1>
According to the first embodiment, the twin rotary compressor 100 includes the electric motor 103 having the stator 103a and the rotor 103b. The twin rotary compressor 100 has a first eccentric portion 104b provided on the main shaft 104a fixed to the rotor 103b and a second eccentric portion 104c provided on the main shaft 104a, and is rotated by the electric motor 103. The crankshaft 104 is provided. The twin rotary compressor 100 includes a first piston 105a provided on the first eccentric portion 104b. The twin rotary compressor 100 includes a second piston provided on the second eccentric portion 104c. The twin rotary compressor 100 includes a first cylinder 107a in which a cylindrical through hole is formed and the first eccentric portion 104b and the first piston 105a are arranged in the through hole to form a first compression chamber 106a. Prepare The twin rotary compressor 100 includes a second cylinder 107b in which a cylindrical through hole is formed, and the second eccentric portion 104c and the second piston are arranged in the through hole to form a second compression chamber. The twin rotary compressor 100 includes an injection flow passage 205 for injecting a refrigerant into each of the first compression chamber 106a and the second compression chamber from the refrigerant pipe 204 in front of the evaporator 203 in the refrigerant circulation direction of the refrigeration cycle circuit. The injection flow path 205 has a first injection port 205a1 formed in the first compression chamber 106a. The injection flow path 205 has a second injection port 205a2 formed in the second compression chamber. The injection flow path 205 has an injection inlet pipe 205b connected to the refrigerant pipe 204. The injection flow path 205 has a first injection pipe 205c that supplies a refrigerant to the first injection port 205a1. The injection flow path 205 has a second injection pipe 205d that supplies a refrigerant to the second injection port 205a2. The injection flow passage 205 is arranged between the injection inlet pipe 205b and the first injection pipe 205c and the second injection pipe 205d, and the injection muffler has a diameter larger than the inner diameters of the first injection pipe 205c and the second injection pipe 205d. 205e. The first injection pipe 205c and the second injection pipe 205d are separately connected to the injection muffler 205e.

According to this structure, it is arranged between the injection inlet pipe 205b and the first injection pipe 205c and the second injection pipe 205d, and has a diameter larger than the inner diameter of each of the first injection pipe 205c and the second injection pipe 205d. It has an injection muffler 205e. The first injection pipe 205c and the second injection pipe 205d are separately connected to the injection muffler 205e. Therefore, the pressure fluctuation generated in the first compression chamber 106a and the second compression chamber and the pressure pulsation of the injection refrigerant can be absorbed, and the supercharging effect of increasing the flow rate of the injection refrigerant can be exhibited. Therefore, the twin rotary compressor 100 becomes highly efficient.

Further, the injection refrigerant is separately injected from the injection muffler 205e into the first compression chamber 106a and the second compression chamber by the first injection pipe 205c and the second injection pipe 205d, respectively. As a result, it is possible to prevent the refrigerant from leaking from one compression chamber to the other compression chamber due to the pressure difference between the first compression chamber 106a and the second compression chamber, and reduce the deterioration of the compressor performance.

According to the first embodiment, the first injection pipe 205c and the second injection pipe 205d project upward into the injection muffler 205e at the lower part of the injection muffler 205e.

With this configuration, the first injection pipe 205c and the second injection pipe 205d can be easily connected to the injection muffler 205e in terms of processing.

According to the first embodiment, the injection inlet pipe 205b is separated from the first injection pipe 205c and the second injection pipe 205d protruding upward into the injection muffler 205e at the upper part of the injection muffler 205e, and inside the injection muffler 205e. Protruding downwards.

According to this configuration, the pressure fluctuations generated in the first compression chamber 106a and the second compression chamber and the pressure pulsation of the injection refrigerant can be absorbed, and the supercharging effect of increasing the flow rate of the injection refrigerant can be exhibited.

According to the first embodiment, the protrusion amounts B, B1 and B2 by which the first injection pipe 205c and the second injection pipe 205d protrude in the injection muffler 205e have a length that allows injection of either a gas refrigerant or a liquid refrigerant. Have.

With this configuration, even if the liquid refrigerant falls to the lower layer in the injection muffler 205e, the injection of the liquid refrigerant can be performed. Moreover, in injection of a gas refrigerant, there is no condition like a liquid refrigerant. As a result, injection can be performed with either a gas refrigerant or a liquid refrigerant.

According to the first embodiment, in the twin rotary compressor 100 described above, the supercharging rate α [%] represented by the following relational expression (Equation 1), where the supercharging rate α exceeds 100%, the following L A first injection pipe 205c and a second injection pipe 205d having a combination of [m] and d[m] below are provided.
α=K×(L/d ⁵ )... (Formula 1)
Here, α [%] is a value of α>100%, and the pressure loss ΔP in the case where there is a supercharging effect in each of the first injection pipe 205c and the second injection pipe 205d is equal to the first injection pipe. The pressure loss Pbase [Pa] when there is no supercharging effect in each of 205c and the second injection pipe 205d is divided and multiplied by 100, and 100% is obtained in each of the first injection pipe 205c and the second injection pipe 205d. It is the supercharging rate when there is a supercharging effect exceeding.
L[m] is the length of each of the first injection pipe 205c and the second injection pipe 205d.
d[m] is the inner diameter of each of the first injection pipe 205c and the second injection pipe 205d.
K [kg·m ³ /(s ² ·Pa)] is a coefficient that replaces J×100/Pbase and has a correlation with λ, ρ, Q, and Pbase.
J [kg·m ³ /s ² ] is a coefficient having a correlation with λ, ρ, and Q, in which (8/π ² ×λ×ρ×Q ² ) is replaced.

With this configuration, the pressure fluctuation generated in the compression chamber and the pressure pulsation of the injection refrigerant by the injection muffler 205e can be absorbed from each of the first injection pipe 205c or the second injection pipe 205d. Along with this, the length L of each of the first injection pipe 205c or the second injection pipe 205d and the inner diameter d of each of the first injection pipe 205c or the second injection pipe 205d are correlated with the supercharging rate α. Depending on the relationship, it is possible to design the dimensions such that the supercharging effect of increasing the flow rate of the injection refrigerant is exhibited. Therefore, the pressure fluctuation and the pressure pulsation of the injection refrigerant generated in the compression chamber can be absorbed, and the supercharging effect of increasing the flow rate of the injection refrigerant can be exhibited. Therefore, the twin rotary compressor 100 becomes highly efficient. For example, in the twin rotary compressor 100 of 2 to 10 HP, by setting the length L to 20 to 850 mm and the inner diameter d to φ1 to φ15 mm, a configuration in which the supercharging rate α exceeds 100% can be suitably designed. The above supercharging effect can be suitably exhibited.

According to the first embodiment, twin rotary compressor 100 obtains α in the range of (αmax+1)/2≦α≦αmax, where αmax is the maximum value of α obtained by the combination of L and d. A first injection pipe 205c and a second injection pipe 205d having a combination of L and d are provided.

According to this configuration, the length L of each of the first injection pipe 205c or the second injection pipe 205d and the inner diameter d of each of the first injection pipe 205c or the second injection pipe 205d determines the flow rate of the injection refrigerant. The size can be designed so that the increased supercharging effect can be more effectively exhibited. Therefore, the pressure fluctuation and the pressure pulsation of the injection refrigerant generated in the compression chamber can be absorbed, and the supercharging effect of increasing the flow rate of the injection refrigerant can be more effectively exhibited. And the heating capacity can be improved. Therefore, the twin rotary compressor 100 becomes highly efficient.

According to the first embodiment, when the inner diameters of the first injection pipe 205c and the second injection pipe 205d are different from each other, the supercharging effect of both the first injection pipe 205c and the second injection pipe 205d can be optimized. Can be achieved.

Here, when the projection amount of the two injection pipes into the injection muffler is the same, and the connection outlet heights of the two injection mufflers to the two injection ports are different, the inner diameters of the two injection pipes are the same. When the supercharging effect of one injection pipe is adjusted to the optimum value, the supercharging effect of the other injection pipe deteriorates. However, according to this configuration, the supercharging effect of both the first injection pipe 205c and the second injection pipe 205d is enhanced.

According to the first embodiment, the inner diameters D1 and D2 of the first injection pipe 205c and the second injection pipe 205d are smaller when the lengths of the first injection pipe 205c and the second injection pipe 205d are smaller. It is possible to optimize the supercharging effect of both the injection pipe 205c and the second injection pipe 205d.

With this configuration, the supercharging effect of both the first injection pipe 205c and the second injection pipe 205d can be appropriately enhanced.

According to the first embodiment, at least one of the first injection pipe 205c and the second injection pipe 205d is connected to the first injection port 205a1 or the second injection port 205a2 at the connection portion with the inner diameter D3 of the first injection pipe 205c or When the connection pipe 206 smaller than the inner diameter D1 or D2 of the second injection pipe 205d is provided, the supercharging effect of both the first injection pipe 205c and the second injection pipe 205d can be optimized.

As a design matter of the twin rotary compressor 100, when fixing the injection muffler 205e to a closed container, the condition that the injection muffler, the inlet of the first injection pipe and the inlet of the second injection pipe are provided at a position lower than the container height is provided. is there. That is, the upper limit of L is determined by the closed container. Further, the lower limit of d is determined by the required bending strength. According to this configuration, when L/d ⁵ is increased, the supercharging effect is enhanced. At least one of the connection outlets of the first injection pipe 205c and the second injection pipe 205d is provided with the connection pipe 206 having a different inner diameter D3. As a result, the supercharging effect can be improved.

According to the first embodiment, when the protrusion amounts B1 or B2 of the first injection pipe 205c and the second injection pipe 205d, which protrude in the injection muffler 205e, are different from each other, the first injection pipe 205c and the first injection pipe 205c. The supercharging effect of both of the two injection pipes 205d can be optimized.

Here, when the projection amount of the two injection pipes into the injection muffler is the same, and the connection outlet heights of the two injection mufflers to the two injection ports are different, the inner diameters of the two injection pipes are the same. When the supercharging effect of one injection pipe is adjusted to the optimum value, the supercharging effect of the other injection pipe deteriorates. However, according to this configuration, the supercharging effect of both the first injection pipe 205c and the second injection pipe 205d is enhanced.

According to the first embodiment, the protrusion amount B1 or B2 protruding in the injection muffler 205e of each of the first injection pipe 205c and the second injection pipe 205d is the length of the first injection pipe 205c and the second injection pipe 205d. When the length is shorter and the length is longer, the supercharging effect of both the first injection pipe 205c and the second injection pipe 205d can be optimized.

With this configuration, the supercharging effect of both the first injection pipe 205c and the second injection pipe 205d can be appropriately enhanced.

According to the first embodiment, the twin rotary compressor 100 has the suction muffler 113 in the pipe that supplies the refrigerant to the twin rotary compressor 100. The volume of the injection muffler 205e is 5% or more of the volume of the suction muffler 113.

With this configuration, the relationship between the refrigerant drawn into the twin rotary compressor 100 and the injection refrigerant is not impaired. Therefore, the pressure fluctuation and the pressure pulsation of the injection refrigerant generated in the compression chamber can be absorbed, and the supercharging effect of increasing the flow rate of the injection refrigerant can be exhibited. Therefore, the twin rotary compressor 100 becomes highly efficient.

According to the first embodiment, the injection muffler 205e is fixed to the outer peripheral portion of the closed container 101 of the twin rotary compressor 100.

According to this configuration, since the injection muffler 205e is fixed to the outer peripheral portion of the closed container 101 of the twin rotary compressor 100, pipe vibrations of the first and second injection pipes 205c and 205d can be suppressed. Further, the injection muffler 205e can be handled as a part of the twin rotary compressor 100 and is easy to handle.

Refrigeration cycle device 200 includes twin rotary compressor 100 of the first embodiment.

According to this configuration, the refrigeration cycle apparatus 200 including the twin rotary compressor 100 can absorb the pressure fluctuation and the pressure pulsation of the injection refrigerant that occur in the first compression chamber 106a and the second compression chamber, and reduce the flow rate of the injection refrigerant. The supercharging effect to increase can be exhibited. Therefore, the refrigeration cycle device 200 including the twin rotary compressor 100 has high efficiency.

100 twin rotary compressor, 101 closed container, 101a tubular member, 101b upper end closing member, 101c lower end closing member, 102 pedestal, 103 electric motor, 103a stator, 103b rotor, 104 crankshaft, 104a main shaft, 104b first deviation Core part, 104c second eccentric part, 104d counter shaft, 105a first piston, 105a1 partition member, 106a first compression chamber, 107a first cylinder, 107a1 through hole, 107a2 discharge port, 107b second cylinder, 108a first Inflow refrigerant pipe, 108b second inflow refrigerant pipe, 109a upper bearing, 109b lower bearing, 110 intermediate plate, 111a upper discharge muffler, 111b lower discharge muffler, 112 discharge pipe, 113 suction muffler, 200 refrigeration cycle device, 201 condenser, 202 expansion valve, 203 evaporator, 204 refrigerant piping, 205 injection flow path, 205a1 first injection port, 205a2 second injection port, 205b injection inlet pipe, 205c first injection pipe, 205d second injection pipe, 205e injection muffler, 205f1 first in-machine passage, 205f2 second in-machine passage, 206 connecting pipe.

A twin rotary compressor according to the present invention includes an electric motor having a stator and a rotor, a first eccentric portion provided on a main shaft fixed to the rotor, and a second eccentric portion provided on the main shaft. A crankshaft rotated by the electric motor, a first piston provided in the first eccentric portion, a second piston provided in the second eccentric portion, and a cylindrical through hole. A first cylinder having a first compression chamber formed by arranging the first eccentric portion and the first piston in the through hole; and a cylindrical through hole formed in the through hole. A rotary compressor including a second cylinder in which a second compression chamber is formed by arranging a second eccentric portion and the second piston, wherein the first compression chamber and the An injection flow path for injecting a refrigerant into each of the second compression chambers is provided, and the injection flow path includes a first injection port formed in the first compression chamber and a second injection port formed in the second compression chamber. and ports, one and injection inlet pipe connected to the refrigerant pipe, one a first injection pipe for supplying refrigerant to the first injection port, one for supplying refrigerant to the second injection port A second injection pipe; and one injection inlet pipe and two first injection pipes and two second injection pipes, which are arranged between the first injection pipe and the second injection pipe. And an injection muffler having an expanded diameter, wherein the first injection pipe and the second injection pipe are separately connected to the injection muffler, and project upward in the injection muffler at a lower portion of the injection muffler. The amount of protrusion of the first injection pipe and the second injection pipe in the injection muffler has such a length that both the gas refrigerant and the liquid refrigerant can be injected .

Claims (14)

An electric motor having a stator and a rotor,
A crankshaft having a first eccentric portion provided on a main shaft fixed to the rotor and a second eccentric portion provided on the main shaft, the crankshaft being rotated by the electric motor;
A first piston provided in the first eccentric portion,
A second piston provided in the second eccentric portion,
A first cylinder in which a cylindrical through hole is formed, and in which the first eccentric portion and the first piston are arranged to form a first compression chamber;
A second cylinder in which a cylindrical through hole is formed, and in which the second eccentric portion and the second piston are arranged to form a second compression chamber;
A rotary compressor equipped with
An injection flow path for injecting a refrigerant into each of the first compression chamber and the second compression chamber from an external refrigerant pipe is provided,
The injection flow passage includes a first injection port formed in the first compression chamber, a second injection port formed in the second compression chamber, an injection inlet pipe connected to the refrigerant pipe, and the first injection port. Between a first injection pipe for supplying a refrigerant to a first injection port, a second injection pipe for supplying a refrigerant to the second injection port, and between the injection inlet pipe, the first injection pipe and the second injection pipe. An injection muffler that is arranged and has a diameter larger than the inner diameters of the first injection pipe and the second injection pipe,
The twin rotary compressor in which the first injection pipe and the second injection pipe are separately connected to the injection muffler. The twin rotary compressor according to claim 1, wherein the first injection pipe and the second injection pipe project upward into the injection muffler at a lower portion of the injection muffler. The injection inlet pipe is spaced apart from the first injection pipe and the second injection pipe protruding upward into the injection muffler at an upper portion of the injection muffler, and is projected downward into the injection muffler. Twin rotary compressor described in. The twin rotary compressor according to claim 2 or 3, wherein a protruding amount of the first injection pipe and the second injection pipe protruding in the injection muffler has a length capable of injecting either a gas refrigerant or a liquid refrigerant. .. The twin rotary compressor according to any one of claims 1 to 4,
The supercharging rate α [%] represented by the following relational expression (Equation 1), wherein the supercharging rate α has a combination of the following L [m] and the following d [m] exceeding 100%. A twin rotary compressor including one injection pipe and the second injection pipe.
α=K×(L/d ⁵ )... (Formula 1)
Here, α [%] is a value of α>100%.
L[m] is the length of each of the first injection pipe and the second injection pipe.
d[m] is the inner diameter of each of the first injection pipe and the second injection pipe.
K [kg·m ³ /(s ² ·Pa)] is a coefficient having a correlation with λ, ρ, Q, and Pbase. The twin rotary compressor according to claim 5,
When αmax is the maximum value of α obtained by the combination of L and d,
A twin rotary compressor provided with the first injection pipe and the second injection pipe having a combination of L and d with which α in the range of (αmax+1)/2≦α≦αmax is obtained. The twin rotary compressor according to claim 1, wherein inner diameters of the first injection pipe and the second injection pipe are different from each other. The twin rotary compressor according to claim 7, wherein the inner diameters of the first injection pipe and the second injection pipe are smaller as the lengths of the first injection pipe and the second injection pipe are shorter. At least one of the first injection pipe and the second injection pipe has a connection portion with the first injection port or the second injection port, the inner diameter of which is larger than the inner diameter of the first injection pipe or the second injection pipe. The twin rotary compressor according to claim 1, wherein a small connecting pipe is provided. The protrusion amount which each of the said 1st injection pipe and the said 2nd injection pipe protrudes in the said injection muffler is mutually different, The claim 2 or any one of Claims 3-9 dependent on Claim 2 is described. Twin rotary compressor. The projecting amount of each of the first injection pipe and the second injection pipe projecting in the injection muffler is longer as the length of the first injection pipe and the second injection pipe is shorter. Twin rotary compressor. A suction muffler is provided in a pipe for supplying a refrigerant to the rotary compressor,
The twin rotary compressor according to any one of claims 1 to 11, wherein a volume of the injection muffler is 5% or more of a volume of the suction muffler. The twin rotary compressor according to any one of claims 1 to 12, wherein the injection muffler is fixed to an outer peripheral portion of a closed container of the rotary compressor. A refrigeration cycle apparatus comprising the twin rotary compressor according to any one of claims 1 to 13.

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