WO2019111392A1

WO2019111392A1 - Rotary compressor and refrigeration cycle device

Info

Publication number: WO2019111392A1
Application number: PCT/JP2017/044069
Authority: WO
Inventors: 宏樹長澤; 祐策石部
Original assignee: 三菱電機株式会社
Priority date: 2017-12-07
Filing date: 2017-12-07
Publication date: 2019-06-13
Also published as: KR20200070376A; CN111417783A; JPWO2019111461A1; CZ2020292A3; JP6918138B2; CZ309387B6; CN111417783B; WO2019111461A1; KR102336280B1

Abstract

A rotary compressor comprising an electric motor, a crank shaft, a piston, a cylinder, and an injection flowpath that injects a refrigerant into a compression chamber from a refrigerant pipe in front an evaporator in the refrigerant flow direction of a refrigeration cycle circuit. The injection flowpath has: an injection port formed in the compression chamber; a branch pipe connected to the refrigerant pipe; an injection pipe that supplies refrigerant to the injection port; and an injection muffler arranged between the branch pipe and the injection pipe and having a larger diameter than the inner diameter of the injection pipe.

Description

Rotary compressor and refrigeration cycle apparatus

The present invention relates to a rotary compressor and a refrigeration cycle apparatus provided with an injection flow channel.

Conventionally, the rotary compressor has mounted the electric motor which consists of a rotor and a stator in the upper part in an airtight container. Then, the rotation of the motor is transmitted to the eccentric part provided at the lower part by the crankshaft fixed to the rotor. The eccentric portion is provided with a piston, and the rotation of the crankshaft eccentrically moves the piston to reduce the volume of the compression chamber. Thus, 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, there is known a technique having an injection muffler in the injection flow path (see, for example, Patent Document 1). The injection muffler absorbs pressure fluctuations and pressure pulsations of the injection refrigerant generated in the compression chamber, and is considered to be able to stably and smoothly supply the refrigerant to be injected.

Japanese Utility Model Application Publication No. 1-58046

By the way, in the case of a rotary compressor to which an injection muffler is applied, not only absorption of pressure fluctuation and pressure pulsation of the injection refrigerant generated in the compression chamber can be absorbed, but a supercharging effect of increasing the flow rate of the injection refrigerant is exhibited. It was found.

The present invention is intended to solve the above-mentioned problems, and is capable of absorbing pressure fluctuations and pressure pulsations of the injection refrigerant generated in the compression chamber, and a highly efficient rotary that can exert a supercharging effect of increasing the flow rate of the injection refrigerant. An object of the present invention is to provide a compressor and a refrigeration cycle apparatus.

A rotary compressor according to the present invention includes a motor having a stator and a rotor, and an eccentric portion provided on a main shaft fixed to the rotor, the crankshaft rotated by the motor, and the eccentricity. A rotary compressor comprising: a piston provided at a core portion; and a cylinder having a cylindrical through hole formed therein, the eccentric portion and the piston being disposed in the through hole to form a compression chamber. An injection flow path for injecting a refrigerant into the compression chamber from a refrigerant pipe in front of the evaporator in a refrigerant flow direction of the refrigeration cycle circuit, the injection flow path being an injection port formed in the compression chamber; A branch pipe connected to the refrigerant pipe, an injection pipe for supplying a refrigerant to the injection port, and a space between the branch pipe and the injection pipe And injection muffler is expanded than the inner diameter of the injection pipe is location, and has a.

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

According to the rotary compressor and the refrigeration cycle apparatus according to the present invention, the injection muffler is disposed between the branch pipe and the injection pipe and has a diameter larger than the inner diameter of the injection pipe. Therefore, pressure fluctuation and pressure pulsation of the injection refrigerant generated in the compression chamber can be absorbed, and a supercharging effect of increasing the flow rate of the injection refrigerant can be exhibited. Therefore, the rotary compressor is highly efficient.

FIG. 1 is a refrigerant circuit diagram showing a refrigeration cycle apparatus to which a twin rotary compressor according to 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 which shows the injection port in the compression chamber 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, and the length L of the injection pipe | tube, and the internal diameter d. It is a longitudinal cross-sectional view which shows the twin rotary compressor which concerns on the modification 1 in Embodiment 1 of this invention. It is a longitudinal cross-sectional view which shows the twin rotary compressor which concerns on the modification 2 in Embodiment 1 of this invention. It is a longitudinal cross-sectional view which shows the twin rotary compressor which concerns on the modification 3 in Embodiment 1 of this invention. It is a longitudinal cross-sectional view which shows the twin rotary compressor which concerns on the modification 4 in Embodiment 1 of this invention.

Hereinafter, embodiments of the present invention will be described based on the drawings. In the drawings, the same reference numerals denote the same or corresponding parts, which are common to the whole text of the specification. Further, in the cross sectional view, hatching is appropriately omitted in view of visibility. Furthermore, the form of the component shown in the specification full text is an illustration to the last, and is not limited to these descriptions.

Embodiment 1
<Refrigeration cycle apparatus 200>
FIG. 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 apparatus 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 that has flowed out of the evaporator 203 is drawn into the twin rotary compressor 100 and becomes high temperature and high pressure. The high temperature and pressure refrigerant is condensed in the condenser 201 to become a liquid. The refrigerant that has become a liquid is decompressed and expanded by the expansion valve 202 to be a low temperature 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 a refrigerant from the refrigerant pipe 204 in front of the evaporator 203 and further in front of the expansion valve 202 in the refrigerant flow direction of the refrigeration cycle circuit. Details of the injection channel 205 will be described later.

The twin rotary compressor 100 described later can be applied to such a refrigeration cycle apparatus 200. In addition, as refrigeration cycle apparatus 200, an air conditioning apparatus, a freezer, or a water heater etc. are mentioned, for example.

<Configuration of Twin Rotary Compressor 100>
FIG. 2 is a longitudinal sectional view showing a twin rotary compressor 100 according to Embodiment 1 of the present invention. FIG. 3 is a cross-sectional view showing an injection port in a compression chamber according to Embodiment 1 of the present invention.

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

An electric motor 103 is disposed in the upper part of the closed container 101. The motor 103 has a stator 103a and a rotor 103b. The stator 103 a of the motor 103 has a cylindrical shape and is fixed to the inner peripheral wall portion of the sealed container 101. The rotor 103 b has a cylindrical shape, and is rotatably disposed in the hollow portion formed at the center of the stator 103 a in the horizontal direction and in the circumferential direction.

In the sealed container 101, a crankshaft 104 rotated by an electric motor 103 is disposed extending in the vertical direction. The crankshaft 104 has a main shaft 104a, a first eccentric portion 104b, a second eccentric portion 104c, and an auxiliary 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 portion 104b is provided on the main shaft 104a on the side of the main shaft 104a above the second eccentric portion 104c, decenters the center line from the main shaft 104a, and is larger than the main shaft 104a. The second eccentric portion 104c is provided on the main shaft 104a on the side of the secondary shaft 104d below the first eccentric portion 104b, and the central axis is eccentric with the main shaft 104a and the first eccentric portion 104b, and is larger than the main shaft 104a. .

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

The first eccentric portion 104b and the first piston 105a are disposed in a first cylinder 107a in which a cylindrical through hole is formed. In the first cylinder 107a, the first eccentric portion 104b and the first piston 105a are disposed in the through hole to form a first compression chamber 106a. The first compression chamber 106 a is a sealed cylindrical space. The first inflow refrigerant pipe 108a is connected to the first cylinder 107a via the through hole 107a1.

Further, as in FIG. 3, the second eccentric portion 104 c 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 disposed in a second cylinder 107b in which a cylindrical through hole is formed below the first cylinder 107a. In the second cylinder 107b, a second eccentric portion 104c and a second piston are disposed in the through hole to form a second compression chamber. The second compression chamber is a sealed cylindrical space. The second inflow refrigerant pipe 108b is connected to the second cylinder 107b through the through hole.

At the upper end of the first cylinder 107a, an upper bearing 109a that constitutes the upper wall portion of the first compression chamber 106a is provided while slidably holding the crankshaft 104.

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

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

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

The first inflow refrigerant pipe 108 a and the second inflow refrigerant pipe 108 b have both inlets inserted into the suction muffler 113. The suction muffler 113 is connected to the refrigerant pipe 204 of the refrigeration cycle circuit to allow the refrigerant to flow therein. The suction muffler 113 is fixed to the outer periphery of the closed container 101.

<Operation of Twin Rotary Compressor 100>
Refrigerant oil is accumulated at the bottom of the sealed container 101. The refrigeration oil accumulated at the bottom is sucked up from the hollow hole provided in the crankshaft 104 by the rotation of the crankshaft 104 in the manner of a centrifugal pump utilizing the rotation of the crankshaft 104. The pumped refrigeration 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 machine part is sealed by the refrigerator oil. For this reason, the sliding parts, 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 do not come into direct contact with each other. Damage is prevented and leakage of the refrigerant is further prevented.

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

In the twin rotary compressor 100, the crankshaft 104 fixed to the rotor 103b of the motor part is rotated by the motor 103. Thus, the first eccentric portion 104b and the second eccentric portion 104c, and the first piston 105a and the second piston attached to the outer peripheral portion of the first eccentric portion 104b and the second eccentric portion 104c, respectively, Eccentric rotation. Then, the volumes of the first compression chamber 106 a and the second compression chamber are reduced, and the refrigerant is compressed to change to a high pressure.

<Details of Injection Channel 205>
As shown in FIG. 1, the injection flow path 205 is formed by the refrigerant piping 204 in front of the evaporator 203 and further in front of the expansion valve 202 in the refrigerant flow direction of the refrigeration cycle circuit, and the first compression chamber 106 a and the second compression chamber. Inject the refrigerant into the

The injection flow path 205 includes a first injection port 205a1, a second injection port 205a2, a branch pipe 205b, a first injection pipe 205c, a second injection pipe 205d, an injection muffler 205e, and a first in-machine passage 205f1. , And the second in-machine passage 205 f 2.

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. 1, the branch pipe 205b is connected to the refrigerant pipe 204 of the refrigeration cycle circuit and to the injection muffler 205e.

The first injection pipe 205c has an inlet connected to 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 inlet connected to the injection muffler 205e, is connected to the second in-machine passage 205f2, and supplies the refrigerant to the second injection port 205a2. The second injection pipe 205d is longer than the first injection pipe 205c because the second injection pipe 205d is connected to the lower part of the sealed container 101 than the first injection pipe 205c.

The injection muffler 205e is disposed between the branch pipe 205b and the first injection pipe 205c and the second injection pipe 205d. The inner diameter of the injection muffler 205e is larger than the inner diameter of the first injection pipe 205c and the second injection pipe 205d. Thus, the first injection pipe 205c and the second injection pipe 205d are inserted into the circular bottom of the injection muffler 205e at two places.

The injection muffler 205 e is fixed to the outer peripheral portion of the closed container 101 in the same manner as the suction muffler 113. The volume of the injection muffler 205 e 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 in the lower bearing 109b.

<Operation of Injection Channel 205>
The refrigerant flowing from the refrigeration cycle circuit to the injection flow passage 205 flows into the injection muffler 205e through the branch 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 inside of 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 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 is the pressure of the injection pressure from the refrigeration cycle circuit and the pressure of the first injection pipe 205c and the second injection pipe 205d supplied to the first compression chamber 106a and the second compression chamber. It is intermediate pressure. For this reason, the leakage of the refrigerant due to the pressure difference between the first compression chamber 106a and the second compression chamber is less likely to occur.

The pressure of the first injection pipe 205c and the second injection pipe 205d fluctuates according to the phase 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 branch pipe 205b via the injection muffler 205e which maintains the internal pressure at an intermediate pressure. Therefore, the pressure of the branch pipe 205b is kept constant, whereby the refrigerant injected from the injection flow path 205 is stabilized and the loss is small.

<Features of Injection Channel 205>
In addition to the above, the shape of the injection muffler 205e or the dimensions of the length and the inner diameter of the first injection pipe 205c and the second injection pipe 205d are specified and designed. Thereby, the supercharging effect can be obtained at the time of suction of the injection refrigerant. As a result, the flow rate of the injection refrigerant increases, and the injection refrigerant can be injected with high efficiency.

Here, the inventors obtained the following findings. That is, the supercharging is caused by the amplification of pressure fluctuations of the inlet and the outlet of the first injection pipe 205c and the second injection pipe 205d for drawing the refrigerant. The reason why pressure fluctuations at the inlet and the outlet of the first injection pipe 205c and the second injection pipe 205d are different from each other is a pipe generated when the refrigerant passes through the injection muffler 205e, the first injection pipe 205c or the second injection pipe 205d. Attributable to friction loss. Therefore, the rate of supercharging correlates with the equation of pressure loss due to tube friction loss.

The tube friction coefficient of all the first and

second injection tubes

205c and 205d is defined as λ. The length of each of the first and

second injection pipes

205c and 205d is defined as L [m]. Here, the length L is the length between the end of the first and

second injection tubes

205c and 205d exposed to the outside from the injection muffler 205e and the end exposed to the outside of the sealed container 101. . Although the first and

second injection pipes

205c and 205d are actually inserted into the injection muffler 205e and the closed vessel 101, the length L here is the length of the center line of the portion exposed to the outside. . The inner diameter of each of the first and

second injection tubes

205c and 205d is defined as d [m]. The flow rate of the refrigerant flowing through each of all the first and

second injection pipes

205c and 205d is defined as v [m / s]. The density of the refrigerant flowing through each of all the first and

second injection pipes

205c and 205d is defined as [[kg / m]. At this time, the pressure loss ΔP [Pa] at each outlet of all the first and

second injection pipes

205c and 205d is
ΔP = λ × (L / d) × 1⁄2 × ρ × v ²

Here, the flow rate of the refrigerant flowing through each of all the first and

second injection pipes

205c and 205d is defined as Q [m ³ / s]. The cross-sectional area of each of all the first and

second injection tubes

205c and 205d is defined as (d / 2) ² × π. In that case, since the refrigerant flow velocity 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 ).

Furthermore, when (8 / π ² × λ × ρ × Q ² ) is replaced with a coefficient J [kg · m ³ / s ² ] correlated with λ, 、, Q, ΔP is
ΔP = J × (L / d ⁵ ).

Here, ΔP is divided by the pressure loss Pbase [Pa] when there is no supercharging effect in each of all the first and

second injection pipes

205c and 205d, and multiplied by 100 to obtain all the first, second and third When the supercharging rate α [%] is calculated, which is the maximum value of αmax when there is a supercharging effect in each of the second injection pipes, α is
α = ΔP / Pbase × 100 = J × 100 / Pbase × (L / d ⁵ ).
The supercharging rate α is obtained as an increase rate when the case of no supercharging effect is 100%.

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

That is, there is a correlation between α and L, d using a 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 using the following relational expressions (Expression 2) and (Expression 3).
L = (α × d ⁵ ) / K (Equation 2)
d = (K × L / α) ^1/5 (Equation 3)

FIG. 4 is a view showing the 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. 4, in order to obtain a supercharging effect further, it is more preferable that the length L and the inner diameter d of the first and

second injection pipes

205 c and 205 d satisfy the following relationship.
L is in the range of (αmax + 1) / 2 ≦ α ≦ αmax while satisfying the above-mentioned relational expression (Expression 2) obtained by modifying (Expression 1).
d is a range of (αmax + 1) / 2 ≦ α ≦ αmax while satisfying the above (Expression 3) which is a modification of (Expression 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 = 0.211 [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 205 e 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-described relational expression (Expression 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 205 d is α = 123.7%. As described above, the conditions for exerting a 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, pressure fluctuations and pressure pulsations of the injection refrigerant generated in the first compression chamber 106a and the second compression chamber can be absorbed, and a supercharging effect of increasing the flow rate of the injection refrigerant can be exhibited. Therefore, the twin rotary compressor 100 is highly efficient.

<Modification 1>
FIG. 5 is a longitudinal sectional view showing a twin rotary compressor 100 according to a first modification of the first embodiment of the present invention. In the first modification, the description of the same matters as those of the above-described embodiment will be omitted, and only the characteristic portions will be described.

As shown in FIG. 5, in the twin rotary compressor 100, the connection points of the outlets of the first and

second injection pipes

205c and 205d are different from those in the above embodiment. That is, the outlet of the first injection pipe 205 c 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. 6 is a longitudinal sectional view showing a twin rotary compressor 100 according to Modification 2 of Embodiment 1 of the present invention. In the second modification, the description of the same matters as those in the above-described embodiment will be omitted, and only the characteristic portions will be described.

As shown in FIG. 6, in the twin rotary compressor 100, the connection points of the outlets of the first and

second injection pipes

205c and 205d are different from those in the above 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 205 d is connected to the passage in the intermediate plate 110.

<Modification 3>
FIG. 7 is a longitudinal sectional view showing a twin rotary compressor 100 according to Modification 3 of Embodiment 1 of the present invention. In the third modification, the description of the same matters as those in the above-described embodiment will be omitted, and only the characteristic portions will be described.

As shown in FIG. 7, in the twin rotary compressor 100, the connection points of the outlets of the first and

second injection pipes

205c and 205d are different from those in the above embodiment. That is, the outlets of the first and

second injection pipes

205c and 205d are connected to either the first cylinder 107a or the second cylinder 107b in a circumferentially displaced position, and the upper bearing 109a or the lower bearing 109b from the inside thereof. It is connected to the inner passage and the passage in the middle plate 110 respectively.

<Modification 4>
FIG. 8 is a longitudinal sectional view showing a twin rotary compressor 100 according to Modification 4 in Embodiment 1 of the present invention. In the fourth modification, the description of the same matters as those in the above-described embodiment will be omitted, and only the characteristic portions will be described.

As shown in FIG. 8, in the twin rotary compressor 100, the connection points of the outlets of the first and

second injection pipes

205c and 205d are different from those in the above embodiment. That is, the outlet of the first injection pipe 205c is connected to the first cylinder 107a, and is connected to the passage in the upper bearing 109a from the inside thereof. 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 thereof.

In the first embodiment, the twin rotary compressor in which two compression chambers are present has been described. However, the features of the first embodiment hold even in a single rotary compressor having one compression chamber.

<Effect of Embodiment 1>
According to Embodiment 1, a twin rotary compressor 100 as a rotary compressor includes an electric motor 103 having a stator 103a and a rotor 103b. The twin rotary compressor 100 has first and second

eccentric parts

104b and 104c as eccentric parts provided on the main shaft 104a fixed to the rotor 103b, and the crankshaft 104 rotated by the electric motor 103 is Prepare. The twin rotary compressor 100 includes first and second pistons 105a as pistons provided to the first and second

eccentric portions

104b and 104c. In the twin rotary compressor 100, a cylindrical through hole is formed, and the first and second

eccentric parts

104b and 104c and the first and second pistons 105a are respectively disposed in the through hole to form a first compression chamber. First and

second cylinders

107a and 107b as cylinders in which the first and second compression chambers 106a are formed. The twin rotary compressor 100 includes an injection flow path 205 for injecting a refrigerant into the first and second compression chambers 106 a from the refrigerant pipe 204 in front of the evaporator 203 in the refrigerant flow direction of the refrigeration cycle circuit. The injection flow channel 205 has first and second injection ports 205a1 and 205a2 as injection ports formed in the first and second compression chambers 106a. The injection flow path 205 has a branch pipe 205 b connected to the refrigerant pipe 204. The injection flow channel 205 has first and

second injection pipes

205c and 205d as injection pipes for supplying the refrigerant to the first and second injection ports 205a1 and 205a2. The injection flow path 205 includes an injection muffler 205e disposed between the branch pipe 205b and the first and

second injection pipes

205c and 205d and having a diameter larger than the inner diameter of the first and

second injection pipes

205c and 205d. .

According to this configuration, the injection muffler 205e is disposed between the branch pipe 205b and the first and

second injection pipes

205c and 205d and has a diameter larger than the inner diameter of the first and

second injection pipes

205c and 205d. . Therefore, the pressure fluctuation and the pressure pulsation of the injection refrigerant generated in the first and second compression chambers 106a 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 is highly efficient.

According to the first embodiment, the first and second

eccentric parts

104b and 104c as eccentric parts, the first and second pistons 105a as pistons, and the first and

second cylinders

107a and 107b as cylinders. And two first and

second injection pipes

205c and 205d as injection pipes. The two first and

second injection pipes

205c and 205d are formed in the two first and

second cylinders

107a and 107b respectively, and the first and second injections of the two first and second compression chambers 106a, respectively. A refrigerant flow path leading to the ports 205a1 and 205a2 is formed.

second injection pipes

Further, the injection refrigerant is injected from the injection muffler 205e into the two first and second compression chambers 106a by the two first and

second injection pipes

205c and 205d, respectively. As a result, the pressure difference between the two first and second compression chambers 106a prevents the refrigerant from leaking from one compression chamber to the other, thereby reducing the reduction in compressor performance.

According to Embodiment 1, a twin rotary compressor 100 as a rotary compressor includes an electric motor 103 having a stator 103a and a 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. A crankshaft 104 is provided. The twin rotary compressor 100 includes a first piston 105 a provided to the first eccentric portion 104 b. The twin rotary compressor 100 includes a second piston provided to the second eccentric portion 104c. In the twin rotary compressor 100, a cylindrical through hole is formed, and the first eccentric portion 104b and the first piston 105a are disposed in the through hole to form a first cylinder 107a in which a first compression chamber 106a is formed. Prepare. The twin rotary compressor 100 is provided with a second cylinder 107b in which a cylindrical through hole is formed, a second eccentric portion 104c and a second piston are disposed in the through hole, and a second compression chamber is formed. The twin rotary compressor 100 includes an injection flow path 205 for injecting the refrigerant from the refrigerant pipe 204 in front of the evaporator 203 in the refrigerant flow direction of the refrigeration cycle circuit into each of the first compression chamber 106 a and the second compression chamber. The injection flow channel 205 has a first injection port 205a1 formed in the first compression chamber 106a. The injection channel 205 has a second injection port 205a2 formed in the second compression chamber. The injection flow path 205 has a branch pipe 205 b connected to the refrigerant pipe 204. The injection flow path 205 has a first injection pipe 205c for supplying a refrigerant to the first injection port 205a1. The injection flow path 205 has a second injection pipe 205d for supplying the refrigerant to the second injection port 205a2. The injection flow path 205 is disposed between the branch pipe 205b and the first injection pipe 205c and the second injection pipe 205d, and the injection muffler 205e has a diameter larger than the inner diameter of the first injection pipe 205c and the second injection pipe 205d. Have.

According to this configuration, the injection disposed between the branch pipe 205b and the first injection pipe 205c and the second injection pipe 205d and having a diameter larger than the inner diameters of the first injection pipe 205c and the second injection pipe 205d. It has a muffler 205e. Therefore, pressure fluctuations and pressure pulsations of the injection refrigerant generated in the first compression chamber 106a and the second compression chamber can be absorbed, and a supercharging effect of increasing the flow rate of the injection refrigerant can be exhibited. Therefore, the twin rotary compressor 100 is highly efficient.

Further, the injection refrigerant is injected from the injection muffler 205e into the first compression chamber 106a and the second compression chamber through the first injection pipe 205c and the second injection pipe 205d, respectively. As a result, the pressure difference between the first compression chamber 106 a and the second compression chamber prevents the refrigerant from leaking from one compression chamber to the other compression chamber, and the reduction in compressor performance can be reduced.

According to the first embodiment, in the twin rotary compressor 100 as the above-described rotary compressor, the following relational expression (Expression 1) is satisfied.
α = K × (L / d ⁵ ) (Equation 1)
Here, α [%] has αmax as the maximum value, and the pressure loss ΔP when there is a supercharging effect in each of all the first and

second injection pipes

205c and 205d The pressure loss Pbase [Pa] when there is no supercharging effect in each of the 2

injection pipes

205c and 205d is divided and multiplied by 100, and supercharging is performed in each of all the first and

second injection pipes

205c and 205d. It is the supercharging rate when there is an effect.
L [m] is the length of each of the first and

second injection pipes

205c and 205d.
d [m] is the inner diameter of each of the first and

second injection pipes

205c and 205d.
K [kg · m ³ / (s ² · Pa)] is a coefficient having correlation with λ, 、, Q, Pbase, in which J × 100 / Pbase is replaced.
J [kg · m ³ / s ² ] is a coefficient having correlation with λ, 、, and Q, in which (8 / π ² × λ × ρ × Q ² ) is replaced.

According to this configuration, the pressure fluctuation generated in the compression chamber and the pressure pulsation of the injection refrigerant can be absorbed by the injection muffler 205e. In addition, the length L of each of the first and

second injection pipes

205c and 205d and the inner diameter d of each of the first and

second injection pipes

205c and 205d are correlated with the supercharging rate α. The size can be designed such that the supercharging effect of increasing the flow rate of the injection refrigerant can be exhibited. Therefore, pressure fluctuation and pressure pulsation of the injection refrigerant generated in the compression chamber can be absorbed, and a supercharging effect of increasing the flow rate of the injection refrigerant can be exhibited. Therefore, the twin rotary compressor 100 is highly efficient.

According to Embodiment 1, in the twin rotary compressor 100, L is in the range of (αmax + 1) / 2 ≦ α ≦ αmax while satisfying the following relational expression (Expression 2) obtained by modifying (Expression 1). d is the range of (αmax + 1) / 2 ≦ α ≦ αmax while satisfying the following (Expression 3) which is a modification of (Expression 1).
L = (α × d ⁵ ) / K (Equation 2)
d = (K × L / α) ^1/5 (Equation 3)

According to this configuration, the respective lengths L of the first and

second injection pipes

205c and 205d and the respective inner diameters d of the first and

second injection pipes

205c and 205d increase the flow rate of the injection refrigerant. It can be designed to a size that can exert the supercharging effect more effectively. 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. Therefore, the twin rotary compressor 100 is highly efficient.

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

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

According to the first embodiment, the injection muffler 205 e is fixed to the outer peripheral portion of the hermetic 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 hermetic container 101 of the twin rotary compressor 100, the piping vibration of the first and

second injection pipes

205c and 205d can be suppressed. In addition, the injection muffler 205e can be handled as part of the twin rotary compressor 100 and is easy to handle.

The refrigeration cycle apparatus 200 includes the twin rotary compressor 100 according to the first embodiment.

According to this configuration, the refrigeration cycle apparatus 200 including the twin rotary compressor 100 can absorb pressure fluctuations and pressure pulsations of the injection refrigerant generated in the first compression chamber 106a and the second compression chamber, and the flow rate of the injection refrigerant The supercharge effect to increase can be exhibited. Therefore, the refrigeration cycle apparatus 200 including the twin rotary compressor 100 is highly efficient.

DESCRIPTION OF SYMBOLS 100 twin rotary compressor, 101 closed container, 101a cylindrical member, 101b upper end closing member, 101c lower end closing member, 102 pedestal, 103 motor, 103a stator, 103b rotor, 104 crankshaft, 104a main shaft, 104b first bias Core part, 104c second eccentric part, 104d countershaft, 105a first piston, 105a1 partition member, 106a first compression chamber, 107a first cylinder, 107a1 through hole, 107a2 outlet, 107b second cylinder, 108a first Inflow refrigerant piping, 108b second inflow refrigerant piping, 109a upper bearing, 109b lower bearing, 110 middle plate, 111a upper discharge muffler, 111b lower discharge muffler, 112 discharge pipe, 113 suction muffler, 200 refrigeration cycle device, 2 Reference Signs List 1 condenser, 202 expansion valve, 203 evaporator, 204 refrigerant pipe, 205 injection flow path, 205a1 first injection port, 205a2 second injection port, 205b branch pipe, 205c first injection pipe, 205d second injection pipe, 205e Injection muffler, 205f1 1st machine passage, 205f 2 2nd machine passage.

Claims

A motor having a stator and a rotor;
A crankshaft having an eccentric portion provided on a main shaft fixed to the rotor, and rotated by the motor;
A piston provided at the eccentric portion;
A cylinder in which a cylindrical through hole is formed, the eccentric part and the piston are disposed in the through hole, and a compression chamber is formed;
A rotary compressor equipped with
It has an injection flow path for injecting the refrigerant into the compression chamber from the refrigerant pipe in front of the evaporator in the refrigerant flow direction of the refrigeration cycle circuit,
The injection flow path includes an injection port formed in the compression chamber, a branch pipe connected to the refrigerant pipe, an injection pipe for supplying a refrigerant to the injection port, and a space between the branch pipe and the injection pipe. A rotary compressor having an injection muffler disposed at an inner diameter of the injection pipe and being larger than the inner diameter of the injection pipe.
Two of the eccentric portion, the piston, the cylinder, and the injection pipe are provided,
2. The rotary compressor according to claim 1, wherein the two injection pipes form refrigerant flow paths leading to respective injection ports of the two compression chambers respectively formed in the two cylinders. 3.
A 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 motor;
A first piston provided to the first eccentric portion;
A second piston provided at the second eccentric portion;
A first cylinder in which a cylindrical through hole is formed, and the first eccentric portion and the first piston are arranged in the through hole to form a first compression chamber;
A second cylinder in which a cylindrical through hole is formed, and the second eccentric portion and the second piston are disposed in the through hole to form a second compression chamber;
A rotary compressor equipped with
It has an injection flow path for injecting a refrigerant from each of the first compression chamber and the second compression chamber from the refrigerant pipe in front of the evaporator in the refrigerant flow direction of the refrigeration cycle circuit,
The injection flow path includes a first injection port formed in the first compression chamber, a second injection port formed in the second compression chamber, a branch pipe connected to the refrigerant pipe, and the first flow path. A first injection pipe for supplying a refrigerant to the injection port, a second injection pipe for supplying a refrigerant to the second injection port, and the branch pipe and the first injection pipe and the second injection pipe. A rotary compressor having an injection muffler whose diameter is larger than the inner diameter of the first injection pipe and the second injection pipe.
The rotary compressor according to any one of claims 1 to 3, wherein
The rotary compressor which satisfies the following relational expression (formula 1).
α = K × (L / d 5 ) (Equation 1)
Here, α [%] has αmax as the maximum value, and the pressure loss ΔP when there is a supercharging effect in each of all the injection pipes, the supercharging effect in each of all the injection pipes is The pressure loss Pbase [Pa] in the absence case is divided and multiplied by 100, and it is a supercharging rate when there is a supercharging effect in each of all the injection pipes.
L [m] is the length of each of all the injection tubes.
d [m] is the inner diameter of each of the injection tubes.
K [kg · m 3 / (s 2 · Pa)] is a coefficient having correlation with λ, 、, Q, Pbase, in which J × 100 / Pbase is replaced.
J [kg · m 3 / s 2 ] is a coefficient having correlation with λ, 、, and Q, in which (8 / π 2 × λ × ρ × Q 2 ) is replaced.
In the rotary compressor according to claim 4,
L is in the range of (αmax + 1) / 2 ≦ α ≦ αmax, while satisfying the following relational expression (Expression 2) which is a modification of (Expression 1),
The rotary compressor which is a range of ((alpha) max + 1) / 2 <= (alpha) <= (alpha) max, while satisfy | filling the following (Formula 3) which deform | transformed (Formula 1).
L = (α × d 5 ) / K (Equation 2)
d = (K × L / α) 1/5 (Equation 3)
A pipe for supplying a refrigerant to the rotary compressor has a suction muffler,
The rotary compressor according to any one of claims 1 to 5, wherein a volume of the injection muffler is 5% or more of a volume of the suction muffler.
The rotary compressor according to any one of claims 1 to 6, wherein the injection muffler is fixed to an outer peripheral portion of a hermetic container of the rotary compressor.
A refrigeration cycle apparatus comprising the rotary compressor according to any one of claims 1 to 7.