KR20210024153A - Rotary compressor and refrigeration cycle unit - Google Patents

Abstract

The rotary compressor has an electric motor having a stator and a rotor, an eccentric part provided on a main shaft fixed to the rotor, a crank shaft rotated by the motor, a piston provided in the eccentric part, and a cylindrical through hole formed therein. In a rotary compressor having a cylinder in which an eccentric portion and a piston are arranged in a hole to form a compression chamber, an injection flow path for injecting an injection refrigerant into the compression chamber, and a partition portion for closing a through hole in the cylinder, the injection flow path A plurality of injection holes for injecting an injection refrigerant into the compression chamber from within the partition portion, and a common hole formed in the partition portion and communicating with the plurality of injection holes are provided.

Description

Rotary compressor and refrigeration cycle unit

The present invention relates to a rotary compressor and a refrigeration cycle device having a partition portion that closes a through hole in a cylinder.

In a conventional rotary compressor, an electric motor comprising a rotor and a stator is mounted on an upper portion of a sealed container. Then, the rotation of the electric motor is transmitted downward by the crankshaft fixed to the rotor. Below the crankshaft, a compression mechanism is configured. The compression mechanism portion mainly includes a cylinder, a main bearing, a secondary bearing, an intermediate plate, and a piston. In the compression mechanism portion, the eccentric crankshaft rotates, the piston moves eccentrically, and the refrigerant is compressed by reducing the volume of the compression chamber.

Further, in one or more of the main bearing, the secondary bearing, and the intermediate plate, an injection hole for introducing an injection refrigerant is formed so as to communicate with the compression chamber. An intermediate pressure liquid or gas refrigerant is injected into the compression chamber as an injection refrigerant by an injection flow path introduced from the middle of the refrigeration cycle circuit. In addition to the refrigerant intake from the main circuit in the refrigeration cycle circuit, the amount of refrigerant discharged increases, and the refrigerant flow rate on the condenser side of the refrigeration cycle circuit increases, and the heating ability This is improved. Further, the sliding parts forming the compression mechanism are cooled by the injection refrigerant, so that the gap between the sliding parts is properly maintained, thereby improving the reliability of the rotary compressor.

As a twin rotary compressor having an injection flow path, a technique in which an injection flow path is formed in an intermediate plate is known (see, for example, Patent Documents 1 and 2).

Japanese Patent Laid-Open No. 2012-251485 Japanese Patent Laid-Open No. 2016-23582

In order to configure an injection flow path in a twin rotary compressor, it is necessary to form the injection flow path in a partition portion such as a bearing or an intermediate plate. In the bearing or the intermediate plate inside the inner diameter of the cylinder, since the eccentrically moving piston passes, there is a section in which the injection refrigerant does not completely flow. In the section in which the injection refrigerant does not flow, the refrigerant flowing into the compression chamber is only the refrigerant suctioned from the main circuit in the refrigeration cycle circuit. For this reason, the amount of discharged refrigerant decreases, and the injection effect is lowered. In addition, in a section in which the injection coolant does not flow, the sliding parts are not cooled, and reliability cannot be improved.

The present invention is to solve the above problem, and the injection refrigerant always flows into the compression chamber regardless of the eccentric motion of the piston, so that the amount of discharged refrigerant is increased and the injection effect can be obtained, while the sliding parts are always cooled, thereby improving reliability. An object of the present invention is to provide a rotary compressor and a refrigeration cycle device that can be improved.

The rotary compressor according to the present invention includes an electric motor having a stator and a rotor, an eccentric portion provided on a main shaft fixed to the rotor, a crank shaft rotated by the electric motor, a piston provided in the eccentric portion, and a cylindrical shape. A rotary compressor having a cylinder in which an upper through hole is formed, and the eccentric portion and the piston are disposed in the through hole to form a compression chamber, the injection flow path for injecting an injection refrigerant into the compression chamber, and in the cylinder And a partition portion for closing the through hole, and the injection flow path includes a plurality of injection holes for injecting an injection refrigerant into the compression chamber from within the partition portion, and is formed in the partition portion and communicates with the plurality of injection holes. It has a common hole.

The refrigeration cycle device according to the present invention is provided with the rotary compressor described above.

According to the rotary compressor and refrigeration cycle apparatus according to the present invention, the injection flow path has a plurality of injection holes for injecting an injection refrigerant into the compression chamber from within the partition, and a common hole formed in the partition and communicating with the plurality of injection holes. Have. Accordingly, the opening area through which the injection refrigerant is injected into the compression chamber is increased with a simple configuration. In addition, the injection flow path can always communicate with the compression chamber. Accordingly, the injection refrigerant always flows into the compression chamber regardless of the eccentric motion of the piston, so that the amount of discharged refrigerant increases, the injection effect is obtained, and the sliding parts are always cooled, thereby improving reliability.

1 is a refrigerant circuit diagram showing a refrigeration cycle device to which a twin rotary compressor according to Embodiment 1 of the present invention is applied.
2 is an explanatory diagram showing a longitudinal section of a twin rotary compressor according to Embodiment 1 of the present invention.
3 is a side view showing an upper bearing in which a common hole is formed according to Embodiment 1 of the present invention.
Fig. 4 is an explanatory view showing a cross section in which the injection hole opened in the compression chamber according to the first embodiment of the present invention is visible.
Fig. 5 is an explanatory view showing a cross section of an upper bearing in which a common hole and a jet hole are formed according to the first embodiment of the present invention, taken along an AA cross section in Fig.
6 is an explanatory diagram showing a longitudinal section of a piston according to Embodiment 1 of the present invention.
7 is an explanatory view showing an opening state of an injection hole according to an eccentric motion of the piston according to the first embodiment of the present invention in a range of 0° to 360°.
Fig. 8 is an explanatory view showing a cross section in which a spray hole opened in a compression chamber according to Modification Example 1 in Embodiment 1 of the present invention is visible.
9 is an explanatory view showing a longitudinal section of a compression mechanism portion of a twin rotary compressor according to Embodiment 2 of the present invention.
Fig. 10 is an explanatory view showing a cross section of an intermediate plate in which common holes and jetting holes are formed according to Embodiment 2 of the present invention.
Fig. 11 is an explanatory view showing a cross section of an intermediate plate in which common holes and jet holes are formed according to Modification Example 2 in Embodiment 2 of the present invention.
Fig. 12 is an explanatory view showing a cross section in which the injection hole opened in the compression chamber according to the third embodiment of the present invention is visible.
Fig. 13 is an explanatory view showing a cross section in which the injection hole opened in the compression chamber according to the fourth embodiment of the present invention is visible.

Hereinafter, embodiments of the present invention will be described based on the drawings. In addition, in each drawing, what is given the same reference|symbol is the same or equivalent, and this is common in the full text of a specification. In addition, in the drawing of a cross-sectional view, hatching is omitted appropriately in consideration of visibility. In addition, the form of the constituent elements shown in the full text of the specification is merely an example and is not limited to these descriptions.

Embodiment 1

<Refrigeration cycle device 200>

1 is a refrigerant circuit diagram showing a refrigeration cycle device 200 to which a twin rotary compressor 100 according to a first embodiment 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. These twin rotary compressors 100, condensers 201, expansion valves 202, and evaporators 203 are connected through 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 through the accumulator 206 to become high temperature and high pressure. The high temperature and high pressure refrigerant is condensed in the condenser 201 to become a liquid. The refrigerant that has become a liquid is expanded under reduced pressure in the expansion valve 202 to become 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 device 200 transfers the refrigerant to the compression chamber from the separator 207 arranged in the refrigerant pipe 204 immediately in front of the evaporator 203 and in front of the expansion valve 202 in the refrigerant flow direction of the refrigeration cycle circuit. It includes an injection flow path 205 to inject. A control valve 208 that controls the flow rate of the injection refrigerant is provided in the middle of the injection flow path 205. The control valve 208 is disposed in the injection flow path 205 upstream from the twin rotary compressor 100 in the injection refrigerant flow direction. The control valve 208 is composed of, for example, an on-off valve, a check valve, or a flow rate control valve, and adjusts the injection refrigerant flow rate so as to obtain an optimum injection effect. In addition, details of the injection flow path 205 will be described later.

The twin rotary compressor 100 described later can be applied to such a refrigeration cycle device 200. In addition, examples of the refrigeration cycle device 200 include an air conditioner, a refrigeration device, or a hot water heater.

<Configuration of twin rotary compressor 100>

2 is an explanatory diagram showing a longitudinal section of a twin rotary compressor 100 according to Embodiment 1 of the present invention. 3 is a side view showing an upper bearing 109a in which the first common hole 205f1 is formed according to the first embodiment of the present invention. Fig. 4 is an explanatory view showing a cross section in which the first injection hole 205a1 and the second injection hole 205a2 opened in the first compression chamber 106a according to the first embodiment of the present invention are visible. 5 is a cross-sectional view of an upper bearing 109a having a first common hole 205f1, a first injection hole 205a1, and a second injection hole 205a2 according to the first embodiment of the present invention in the AA cross section of FIG. It is an explanatory diagram shown. 6 is an explanatory view showing a longitudinal section of the first piston 105a according to the first embodiment of the present invention.

As shown in Fig. 2, the twin rotary compressor 100 includes a tubular sealed container 101 in which both upper and lower ends are closed. The sealed container 101 includes 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 upper end closing member 101b that closes the lower end of the tubular member 101a. It has a lower closing member 101c. The sealed container 101 is installed and fixed to the pedestal 102.

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

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 a minor 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 side of the main shaft 104a above the second eccentric part 104c, makes the main shaft 104a and the center line eccentric, and is larger than the main shaft 104a. The second eccentric part 104c is provided on the main shaft 104a on the side of the minor shaft 104d below the first eccentric part 104b, and makes the main shaft 104a, the first eccentric part 104b and the center line eccentric, It is larger than the main shaft 104a.

As shown in FIG. 4, the 1st piston 105a is provided in the 1st eccentric part 104b. The first piston 105a has a vane 105a1 partitioning the first compression chamber 106a. The first piston 105a is also referred to as a rolling piston.

The first eccentric portion 104b and the first piston 105a are disposed in a first cylinder 107a in which a cylindrical through hole 107a1 is formed. In the first cylinder 107a, a first eccentric portion 104b and a first piston 105a are disposed in a through hole 107a1 to form a first compression chamber 106a. An upper bearing 109a and an intermediate plate 110 for partitioning the vertical direction of the first compression chamber 106a in the first cylinder 107a are disposed. The upper bearing 109a and the intermediate plate 110 close the through hole in the first cylinder 107a. The first compression chamber 106a is a closed cylindrical space. A first inflow refrigerant pipe 108a is connected to the first cylinder 107a through a through hole 107a1.

Further, as in Fig. 4, a second piston (not shown) is provided in the second eccentric portion 104c. The second piston has a vane partitioning the second compression chamber. The second piston is also referred to as a rolling piston.

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 a through hole to form a second compression chamber. An intermediate plate 110 and a lower bearing 109b for partitioning the vertical direction of the second compression chamber in the second cylinder 107b are disposed. The intermediate plate 110 and the lower bearing 109b close the through hole in the second cylinder 107b. The second compression chamber is a closed cylindrical space. A second inflow refrigerant pipe 108b is connected to the second cylinder 107b through a through hole.

The upper bearing 109a covering the upper end surface of the first cylinder 107a constitutes an upper wall portion of the first compression chamber 106a while holding the crankshaft 104 so as to be able to slide.

The lower bearing 109b covering the lower end surface of the second cylinder 107b constitutes the lower wall portion of the second compression chamber while holding the crankshaft 104 so as to be able to slide.

The intermediate plate 110 disposed between the first cylinder 107a and the second cylinder 107b constitutes a lower wall portion of the first compression chamber 106a and an upper wall portion of the second compression chamber, and the first compression chamber 106a ) And the second compression chamber.

The first inflow refrigerant pipe 108a and the second inflow refrigerant pipe 108b have both inflow ports inserted upwardly in the suction muffler 113. The suction muffler 113 is connected by inserting the refrigerant pipe 204 of the refrigeration cycle circuit downward, and allows the refrigerant to flow in. The suction muffler 113 is fixed to the outer periphery of the sealed container 101.

<Operation of the twin rotary compressor 100>

Refrigerator oil is stored in the bottom of the sealed container 101. The refrigerator oil stored in the bottom portion is sucked up by the method of a centrifugal pump using the rotation of the crankshaft 104 from a hollow hole provided in the crankshaft 104 by the rotation of the crankshaft 104. The refrigeration oil sucked up is circulated to each sliding part through the oil supply hole opened toward the outer circumferential part from the hollow hole of the crankshaft 104. Thereby, the machine part is sealed by the refrigerator oil. For this reason, 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, which are sliding parts, And, since the intermediate plate 110 does not directly contact, damage is prevented, and leakage of refrigerant is prevented.

In the upper part of the crankshaft 104, an oil separator (not shown) is fitted. The oil separator prevents the refrigerant oil from flowing out of the discharge pipe 112 together with the discharged refrigerant. The oil separator closes the flow path with respect to the mixed fluid of the refrigerant and refrigerator oil flowing toward the discharge pipe 112 and collides the refrigerant and the refrigerator oil, thereby suppressing the leakage of the refrigerator oil to the outside of the aircraft.

In the twin rotary compressor 100, the crankshaft 104 fixed to the rotor 103b of the motor part is rotated by the electric motor 103. Accordingly, the first and second pistons 105a and 2 are mounted on the outer peripheries of the first eccentric portion 104b and the second eccentric portion 104c, and the first eccentric portion 104b and the second eccentric portion 104c, respectively. The piston rotates eccentrically. Then, the volumes of the first compression chamber 106a and the second compression chamber partitioned by the vanes 105a1 are reduced, and the refrigerant is compressed to change to high pressure. The first compression chamber 106a and the second compression chamber are provided with discharge valves that are released when the pressure reaches a predetermined pressure or higher. When the discharge valve is opened, the high temperature and high pressure gas refrigerant is discharged into the sealed container 101. The compressed gas refrigerant is discharged into the refrigeration cycle circuit outside the twin rotary compressor through the discharge pipe 112. The working refrigerant is for example R410A refrigerant.

<Details of the injection flow path 205>

As shown in Fig. 1, the injection flow path 205 is from the separator 207 provided in the refrigerant pipe 204 immediately in front of the evaporator 203 and in front of the expansion valve 202 in the refrigerant flow direction of the refrigeration cycle circuit. Refrigerant is injected into each of the first compression chamber 106a and the second compression chamber.

The injection flow path 205 has a first injection hole 205a1, a second injection hole 205a2, a third injection hole 205a3, and a fourth injection hole 205a4, as shown in FIG. 2, A first common hole 205f1, a second common hole 205f2, a bypass tube 205b, a first injection tube 205c, a second injection tube 205d, and an injection muffler 205e. Have.

As shown in FIG. 3, the 1st injection hole 205a1 and the 2nd injection hole 205a2 are formed in the 1st compression chamber 106a by opening part of the upper bearing 109a as a partition part. The first injection hole 205a1 and the second injection hole 205a2 inject the injection refrigerant into the first compression chamber 106a from within the upper bearing 109a.

The first injection hole 205a1 and the second injection hole 205a2 are formed at positions equidistant from the center of the first cylinder 107a. More specifically, the first injection hole 205a1 and the second injection hole 205a2 are formed adjacent to the inner diameter boundary of the first cylinder 107a. More preferably, the first injection hole 205a1 and the second injection hole 205a2 are formed inwardly to the inner diameter boundary of the first cylinder 107a. Thereby, as described later, at least one of the first injection hole 205a1 and the second injection hole 205a2 is always opened in the first compression chamber 106a.

The 3rd injection hole 205a3 and the 4th injection hole 205a4 are formed in the 2nd compression chamber by opening part of the lower bearing 109b as a partition part. The third injection hole 205a3 and the fourth injection hole 205a4 inject the injection refrigerant into the second compression chamber from the inside of the lower bearing 109b.

The third injection hole 205a3 and the fourth injection hole 205a4 are formed at positions equidistant from the center of the second cylinder 107b. More specifically, the third injection hole 205a3 and the fourth injection hole 205a4 are formed adjacent to the inner diameter boundary of the second cylinder 107b. More preferably, the 3rd injection hole 205a3 and the 4th injection hole 205a4 are formed inward to the inner diameter boundary of the 2nd cylinder 107b. Thereby, at least one of the third injection hole 205a3 and the fourth injection hole 205a4 is always opened in the second compression chamber, similar to the first injection hole 205a1 and the second injection hole 205a2.

4, the positions of the first injection hole 205a1 and the second injection hole 205a2, the hole diameter of the first injection hole 205a1 and the second injection hole 205a2, the first piston ( By properly setting the relationship between the outer diameter of 105a) and the inner diameter of the first cylinder 107a, at least one of the first injection hole 205a1 and the second injection hole 205a2 is always opened. Here, description will be made using the configuration in the first cylinder. In addition, the configuration in the second cylinder is also the same.

In Embodiment 1, the inner diameter of the first cylinder 107a is 50 mm. The outer diameter of the first piston 105a is 32 mm. Two of the first injection hole 205a1 and the second injection hole 205a2 are provided. Both the first injection hole 205a1 and the second injection hole 205a2 have a hole diameter of 4 mm. The distances between the centers of the holes of the first injection hole 205a1 and the second injection hole 205a2 from the center of the cylinder are both 22.9 mm. The phases of the first injection hole 205a1 and the second injection hole 205a2 are located at 270° and 180° in the counterclockwise direction with respect to the reference in which the position of the vane 105a1 is 0°.

As shown in Fig. 6, a chamfered R processing 105a3 is located inside the inner diameter boundary of the first piston 105a of the sliding surface 105a2 with respect to the upper bearing 109a of the first piston 105a. It has been implemented. And, the whole of the first injection hole 205a1 and the second injection hole 205a2 is the inner diameter boundary of the first piston 105a of the sliding surface 105a2 with respect to the upper bearing 109a of the first piston 105a It is formed more on the outer diameter side. Thereby, injection of the injection refrigerant from the first injection hole 205a1 and the second injection hole 205a2 into the center hole of the first piston 105a is prevented.

As shown in Figs. 2, 3, and 5, the first common hole 205f1 is formed by cutting out a part of the upper bearing 109a serving as a partition portion into a straight horizontal hole. In the first common hole 205f1, a first injection tube 205c is connected to an opening in the side surface of the upper bearing 109a. The inner end of the first common hole 205f1 is closed and closed. The first common hole 205f1 communicates with the first injection hole 205a1 and the second injection hole 205a2. The 1st common hole 205f1 is 1 with respect to the 1st injection hole 205a1 and the 2nd injection hole 205a2. The first common hole 205f1 is formed by being inserted into the center side of the first cylinder 107a than a tangent line of the inner diameter of the first cylinder 107a.

The second common hole 205f2 is formed by cutting out a part of the lower bearing 109b serving as a partition portion into a straight horizontal hole. In the second common hole 205f2, a second injection tube 205d is connected to an opening in the side surface of the lower bearing 109b. The inner end of the second common hole 205f2 is closed and closed. The second common hole 205f2 is in communication with the third injection hole 205a3 and the fourth injection hole 205a4. The second common hole 205f2 is one with respect to the third injection hole 205a3 and the fourth injection hole 205a4. The second common hole 205f2 is formed by being inserted into the center side of the second cylinder 107b rather than a tangent line of the inner diameter of the second cylinder 107b.

As shown in Figs. 1 and 2, the bypass pipe 205b is connected to the refrigerant pipe 204 of the refrigeration cycle circuit, and is connected to the injection muffler 205e by inserting its tip downward.

The first injection tube 205c is fitted with an inlet in an upward direction in the injection muffler 205e, is connected to the first common hole 205f1, and refrigerant is provided in the first injection hole 205a1 and the second injection hole 205a2. Supply.

The second injection tube 205d has an inlet inserted upward into the injection muffler 205e, is connected to the second common hole 205f2, and is refrigerant in the third injection hole 205a3 and the third injection hole 205a3. Supply. The second injection tube 205d is longer than the first injection tube 205c because it is connected to the lower portion of the sealed container 101 than the first injection tube 205c.

The injection muffler 205e is disposed between the bypass 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 tube 205c and the second injection tube 205d. Thereby, the first injection tube 205c and the second injection tube 205d are fitted in the circular bottom portion of the injection muffler 205e at two places.

The injection muffler 205e is fixed to the outer periphery of the sealed container 101 like the suction muffler 113. The volume of the injection muffler 205e is based on the relationship between the suction refrigerant and the injection refrigerant.

<Operation of the injection flow path 205>

7 shows the opening states of the first injection hole 205a1 and the second injection hole 205a2 according to the eccentric motion of the first piston 105a according to the first embodiment of the present invention in a range of 0° to 360°. It is an explanatory diagram. Here, the state at the time of operation of the first piston 105a will be described. In addition, the same is true for the second piston.

First, when the first piston 105a is located at 0° to 135° in the counterclockwise direction based on the position of the vane 105a1 being 0°, the first injection hole 205a1 and the second injection hole Both sides of 205a2 are open. For this reason, the injection refrigerant flows into the first compression chamber 106a from both of the first injection hole 205a1 and the second injection hole 205a2.

Next, when the first piston 105a is located at 135° to 225° in the counterclockwise direction based on the position of the vane 105a1 being 0°, the first injection hole 205a1 is the first piston The sliding surface 105a2 of 105a is covered and closed. The second injection hole 205a2 remains open. For this reason, the injection refrigerant flows into the first compression chamber 106a only from the second injection hole 205a2.

And, when the first piston 105a is located at 225° to 315° in the counterclockwise direction based on the position of the vane 105a1 being 0°, the second injection hole 205a2 is the first piston ( The sliding surface 105a2 of 105a) is covered and closed. The closed first compression chamber 106a is gradually narrowed, and is discharged as a high-temperature and high-pressure gas refrigerant from the discharge hole 107a3 at a place exceeding a predetermined pressure. On the other hand, the first injection hole 205a1 is opened in the next first compression chamber 106a, and the injection refrigerant is introduced. Thereby, regardless of the eccentric motion of the first piston 105a, one of the first injection hole 205a1 and the second injection hole 205a2 is opened in the first cylinder 107a.

The refrigerant flowing through the injection flow path 205 from the refrigeration cycle circuit flows into the injection muffler 205e through the bypass pipe 205b. The refrigerant flowing into the injection muffler 205e is supplied to the first injection tube 205c and the second injection tube 205d within the injection muffler 205e, respectively. The refrigerant supplied to the first injection tube 205c is passed through the first common hole 205f1 of the twin rotary compressor 100, and from the first injection hole 205a1 and the second injection hole 205a2, the first compression chamber ( 106a) is injected as a liquid or gas refrigerant. The refrigerant supplied to the second injection tube 205d passes through the second common hole 205f2 of the twin rotary compressor 100 and passes through the third injection hole 205a3 and the fourth injection hole 205a4 to the second compression chamber. It is injected as a liquid or gas refrigerant inside.

At this time, the pressure in the injection muffler 205e is the injection pressure from the refrigeration cycle circuit, the first injection tube 205c and the second injection tube 205d supplied to the first compression chamber 106a and the second compression chamber. ) Is the intermediate pressure. For this reason, leakage of the refrigerant due to the differential pressure between the first compression chamber 106a and the second compression chamber is unlikely to occur.

The pressures of the first injection tube 205c and the second injection tube 205d fluctuate depending on the phases of the first piston 105a and the second piston. However, the 1st injection tube 205c and the 2nd injection tube 205d are connected to the bypass tube 205b via the injection muffler 205e which maintains an internal pressure at an intermediate pressure. For this reason, by keeping the pressure of the bypass pipe 205b constant, the refrigerant injected from the injection flow path 205 is stabilized, and the loss is small.

<Effect of the injection flow path 205>

Here, in the case of a conventional twin rotary compressor having one injection hole, there is a period in which the end face of the piston passes through the injection hole and closes the injection hole. For this reason, there is a phase in which the flow of the injection refrigerant stops. If the spray hole is only present at 270°, the spray hole is opened in the range of 0° to 18° and 162° to 360°. In this case, in the period of 19° to 161°, the injection hole is closed and the injection refrigerant does not flow into the compression mechanism part, and an injection effect cannot be expected.

In contrast, in the first embodiment, one of the two first injection holes 205a1 and the second injection holes 205a2 is always opened in the first compression chamber 106a. As a result, the flow of the injection refrigerant is not inhibited, and the injection effect is increased. Further, as the openings of the first injection hole 205a1 and the second injection hole 205a2, a complete opening is preferable. When either of the first injection hole 205a1 or the second injection hole 205a2 is always completely opened, the injection effect is higher. This is the same even in the relationship between the third injection hole 205a3 and the fourth injection hole 205a4.

Further, since the distance between the two first injection holes 205a1 and the second injection holes 205a2 is properly arranged, the pulsation of the refrigerant flowing back from the first injection hole 205a1 and the second injection hole 205a2 is prevented. It is reflected by the first piston 105a, and leakage of refrigerant from the first compression chamber 106a to the suction chamber can be suppressed. This is the same even in the relationship between the third injection hole 205a3 and the fourth injection hole 205a4.

Of the first injection hole 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4, the flow rate of the injection refrigerant is due to the long opening section of one injection hole. Increases, and the injection effect increases. In order to lengthen the opening section clearly geometrically, it is good to make the injection hole extremely spaced from the center of the cylinder. However, if it is disposed outside the inner diameter of the cylinder, the injection flow path 205 is blocked on the inner diameter wall surface of the cylinder, and the injection effect is reduced. In addition, when the inner diameter of the cylinder and the formation of the corners of the bearing end face are inhibited by the injection holes, the sealability by the corners of the piston deteriorates, and the compressor efficiency decreases. It is preferable to arrange the position where the outer periphery of the injection hole is most inscribed from the inner diameter of the cylinder to the inner side of about 0.1 mm to 3 mm.

When a plurality of injection holes are arranged so as to be extremely spaced from the center of the cylinder, the distances of the injection holes from the center of the cylinder may be substantially identical. In addition, it is preferable that the common hole in which the two injection holes communicate with each other has a linear shape arranged to shift from the inner diameter tangent of the cylinder toward the center of the cylinder. Thereby, the common hole communicates the two injection holes with a simple structure. Both the first common hole 205f1 and the second common hole 205f2 in the first embodiment have a linear shape arranged shifted from the inner diameter of the cylinder toward the center of the cylinder, and the distance from the center of the cylinder is 16.2 mm.

By appropriately selecting the inner diameter and the inner diameter chamfering amount of the piston, the injection hole and the central hole in the piston are always in a non-communication relationship. Thereby, inflow of high-pressure refrigerant from the injection flow path 205 into the central hole in the piston is suppressed, and the injection effect is enhanced. In Embodiment 1, the inner diameter of the piston is 22 mm with respect to the outer diameter of 32 mm. The amount of chamfering the inner diameter of the piston is 0.5 mm in the radial direction and 0.2 mm in the height direction. The chamfering amount can further suppress the inflow of the high-pressure refrigerant into the injection flow path 205 by making the height direction larger than the radial direction.

As described above, the injection refrigerant is compressed by providing a plurality of injection holes such as the first injection hole 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4. The total area open to the chamber increases, so that the injection refrigerant having a larger flow rate can be introduced into the compression chamber. In addition, there is only one injection pipe inserted into the compression chamber from the outside of the sealed container 101 for each compression chamber. In Embodiment 1, although a plurality of injection holes are provided in one compression chamber, it is not necessary to provide a plurality of injection pipes. Thereby, the degree of freedom in designing the outside of the sealed container and the periphery of the compression mechanism can be improved.

The intersection of the injection hole and the common hole such as the first injection hole 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4 is disposed inside the inner diameter of the cylinder. have. At this intersection point, one injection hole and one common hole are formed by intersecting in a T-shape. The hole corresponding to the vertical side of the T-shape may be either a spray hole or a common hole. However, one of the at least two injection holes close to the entrance of the common hole corresponds to the hole on the vertical side of the T-shape. In Embodiment 1, all the injection holes are arranged as T-shaped vertical holes.

The injection holes such as the first injection hole 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4 may be circular or non-circular, for example, an elliptical shape. When the injection hole is elliptical, in order to secure the communication section, it is preferable to arrange the long diameter side in the tangential direction of the inner diameter of the cylinder. In Embodiment 1, the injection hole is circular.

The diameters of the plurality of injection holes may be unequal. When the diameter of the injection hole on one side is large, the distribution of the injection refrigerant in the compression chamber is selectively changed. For example, due to the large diameter of the injection hole disposed in the near phase by the vane 105a1, the amount of injection refrigerant that cools the vane 105a1 increases, the thermal expansion of the vane 105a1 is suppressed, and the reliability is high. A twin rotary compressor 100 may be provided.

<Modified Example 1>

Fig. 8 is an explanatory view showing a cross section in which the first injection hole 205a1 and the second injection hole 205a2 opened in the first compression chamber 106a according to Modification Example 1 in the first embodiment of the present invention are visible. to be. In Modified Example 1, descriptions of items similar to those in the above-described embodiment are omitted, and only the characteristic portions thereof are described.

As shown in Fig. 2, the injection refrigerant flows into the upper bearing 109a through the first injection tube 205c. Here, the injection refrigerant pressure Pinj is an intermediate pressure between the suction pressure Ps and the discharge pressure Pd. Ps=0.5 MPaG. Pd=4.0 MPaG. Pinj=1.5MPaG. As shown in Fig. 8, the injection refrigerant flowing into the first cylinder 107a is compressed first from the first injection hole 205a1 and the second injection hole 205a2 through the first common hole 205f1. It is sprayed on the thread 106a. Here, the first injection hole 205a1 and the second injection hole 205a2 are disposed inside the inner diameter of the first cylinder 107a. In Modification 1, the inner diameter of the first cylinder 107a is 50 mm. The hole diameter of the first common hole 205f1 is 3 mm. The distance from the center of the first cylinder 107a to the center of the holes of the first injection hole 205a1 and the second injection hole 205a2 is 22.5 mm. The outer diameter of the first piston 105a is 42 mm. The inner diameter of the first piston 105a is 35 mm. The hole diameter of the first injection hole 205a1 is 2 mm, and the vane 105a1 is arranged at a phase of 270°, which is the revolving direction of the first piston 105a in a counterclockwise direction with the reference of 0°. Moreover, the hole diameter of the 2nd injection hole 205a2 is 3 mm, and it is arrange|positioned at the phase of 280 degree. The mass of the refrigerant discharged from the twin rotary compressor 100 by the injection refrigerant increases, so that the heating capacity of the refrigeration cycle device 200 is improved. Further, since the injection refrigerant is lower than that of the discharge refrigerant, the sliding part, for example, the vane 105a1 is cooled and thermal expansion is suppressed, so that the reliability of the twin rotary compressor 100 can be improved.

<Effect of Embodiment 1>

According to the first embodiment, the twin rotary compressor 100 includes an electric motor 103 having a stator 103a and a rotor 103b. The twin rotary compressor 100 has a first eccentric portion 104b and a second eccentric portion 104c provided on a main shaft 104a fixed to the rotor 103b, and a crank rotated by the electric motor 103 It has a shaft 104. The twin rotary compressor 100 includes a first piston 105a and a second piston provided in a first eccentric portion 104b and a second eccentric portion 104c. The twin rotary compressor 100 has a cylindrical through hole 107a1, a first eccentric portion 104b or a second eccentric portion 104c, and a first piston 105a or a second piston in the through hole 107a1. It is provided with a first cylinder (107a) and a second cylinder (107b) in which the first compression chamber (106a) or the second compression chamber is formed. The twin rotary compressor 100 is an injection flow path for injecting an injection refrigerant into the first compression chamber 106a and the second compression chamber from the refrigerant pipe 204 in front of the evaporator 203 in the refrigerant flow direction of the refrigeration cycle circuit ( 205). The twin rotary compressor 100 is provided with an upper bearing 109a, a lower bearing 109b, and an intermediate plate 110 as partitions for closing a through hole in the first cylinder 107a or the second cylinder. The injection flow path 205 includes a plurality of first injection holes for injecting an injection refrigerant into the first compression chamber 106a or the second compression chamber from within the upper bearing 109a, the lower bearing 109b, or the intermediate plate 110. 205a1), the second injection hole (205a2), the third injection hole (205a3) and the fourth injection hole (205a4), and formed in the upper bearing (109a), the lower bearing (109b) or the intermediate plate (110), a plurality of A first common hole (205f1) and a second common hole (205f2) communicating with the first injection hole (205a1), the second injection hole (205a2), the third injection hole (205a3) and the fourth injection hole (205a4) Has.

According to this configuration, the opening area through which the injection refrigerant is injected into the first compression chamber 106a and the second compression chamber is increased with a simple configuration. In addition, the injection flow path 205 can always communicate with the first compression chamber 106a and the second compression chamber. Therefore, the injection refrigerant always flows into the first compression chamber 106a and the second compression chamber regardless of the eccentric motion of the first piston 105a and the second piston, so that the amount of discharged refrigerant increases and the injection effect is obtained, while at the same time sliding motion. Components are always cooled, which can improve reliability.

According to the first embodiment, at least one of the plurality of first injection holes 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4 is always first compressed. It is opened in the chamber 106a and the second compression chamber.

According to this configuration, the injection flow path 205 can always communicate with the first compression chamber 106a and the second compression chamber regardless of the eccentric movement of the first piston 105a and the second piston.

According to the first embodiment, the plurality of first injection holes 205a1, the second injection holes 205a2, the third injection holes 205a3, and the fourth injection holes 205a4 are the first cylinder 107a and the second cylinder. It is formed at a position equidistant from the center of (107b).

According to this configuration, the opening section of one injection hole becomes longer, the injection flow rate increases, and the injection effect becomes higher.

According to the first embodiment, the plurality of first injection holes 205a1, the second injection holes 205a2, the third injection holes 205a3, and the fourth injection holes 205a4 are the first cylinder 107a and the second cylinder. It is formed adjacent to the inner diameter boundary of (107b).

According to this configuration, the opening section of one injection hole becomes longer, the injection flow rate increases, and the injection effect becomes higher.

According to the first embodiment, the plurality of first injection holes 205a1, the second injection holes 205a2, the third injection holes 205a3, and the fourth injection holes 205a4 are the first cylinder 107a and the second cylinder. It is formed inscribed with the inner diameter boundary of (107b).

According to this configuration, the opening section of one injection hole becomes the longest, the injection flow rate increases, and the injection effect becomes higher.

According to the first embodiment, the first common hole 205f1 and the second common hole 205f2 are the first cylinder 107a and the second cylinder than the tangent line of the inner diameters of the first cylinder 107a and the second cylinder 107b. It is formed by being inserted into the center side of (107b).

According to this configuration, the first common hole 205f1 and the second common hole 205f2 communicate with the plurality of injection holes with a simple structure.

According to the first embodiment, all of the plurality of first injection holes 205a1, the second injection holes 205a2, the third injection holes 205a3, and the fourth injection holes 205a4 are the first piston 105a and The upper bearing 109a, the lower bearing 109b and the intermediate plate 110 of the second piston are formed on the outer diameter side of the sliding surface 105a2 than the inner diameter boundary of the first piston 105a and the second piston. .

According to this configuration, the injection refrigerant does not leak through the center holes of the first piston 105a and the second piston, and the injection refrigerant is not wasted.

According to the first embodiment, the first common hole 205f1 and the second common hole 205f2 are linear.

According to this configuration, processing is easy, and the injection flow path 205 can be formed with a simple structure. Further, the first common hole 205f1 and the second common hole 205f2 may not have a linear shape. For example, the first common hole 205f1 and the second common hole 205f2 may have a curved shape, a linear shape having a bent point in the middle, or a meandering line shape.

According to the first embodiment, the first common hole 205f1 and the second common hole 205f2 are one for the upper bearing 109a, the lower bearing 109b, and the intermediate plate 110.

According to this configuration, the number of processing steps is small, processing is easier, and the injection flow path 205 can be formed with a simple structure.

According to the first embodiment, the partition portion in which the common hole and the plurality of injection holes are formed is an upper bearing 109a or a lower bearing 109b covering an end face of the first cylinder 107a or the second cylinder 107b.

According to this configuration, the opening area through which the injection refrigerant is injected into the first compression chamber 106a and the second compression chamber is increased with a simple configuration. In addition, the injection flow path 205 can always communicate with the first compression chamber 106a and the second compression chamber.

According to the first embodiment, the refrigeration cycle device 200 includes the twin rotary compressor 100 described above.

According to this configuration, in the refrigeration cycle device 200 provided with the twin rotary compressor 100, the injection refrigerant is irrespective of the eccentric motion of the first piston 105a and the second piston, the first compression chamber 106a and the second 2 As it always flows into the compression chamber, the amount of refrigerant discharged is increased and the injection effect is obtained, while the sliding parts are always cooled, thereby improving the reliability.

According to the first embodiment, the refrigeration cycle device 200 has a control valve 208 that controls the flow rate of the injection refrigerant in the middle of the injection flow path 205 on the upstream side of the twin rotary compressor 100 in the flow direction of the injection refrigerant.

According to this configuration, the control valve 208 adjusts the flow rate of the injection refrigerant, so that an optimum injection effect is obtained.

Embodiment 2

9 is an explanatory view showing a longitudinal section of a compression mechanism portion of the twin rotary compressor 100 according to the second embodiment of the present invention. 10 is a first common hole 205f1 and a first injection hole 205a1, a second injection hole 205a2, a third injection hole 205a3, and a fourth injection hole 205a4 according to the second embodiment of the present invention. It is an explanatory diagram showing a cross section of the formed intermediate plate 110. In the second embodiment, description of the same matters as in the above embodiment is omitted, and only the characteristic portions thereof are described.

9 and 10, an injection flow path 205 may be provided in the intermediate plate 110. That is, one of the first common hole 205f1, the first injection hole 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4 are the intermediate plate as a partition ( 110). Since the intermediate plate 110 is disposed between the first cylinder 107a and the second cylinder 107b, the group of the first injection hole 205a1 and the second injection hole 205a2 and the third injection hole The pair of 205a3 and the fourth injection hole 205a4 communicates with one first common hole 205f1. Further, by configuring the intersection of the first common hole 205f1 and each injection hole in a cross shape, the injection flow path 205 can be formed with a simpler configuration. In Embodiment 2, all the intersection points are comprised in a cross shape.

<Modified Example 2>

11 is a first common hole 205f1 and a second common hole 205f2, a first injection hole 205a1, a second injection hole 205a2 according to Modification Example 2 in the second embodiment of the present invention, and FIG. It is an explanatory diagram showing a cross section of the intermediate plate 110 in which the three injection holes 205a3 and the fourth injection holes 205a4 are formed. In Modified Example 2, description of the same matters as in the above embodiment is omitted, and only the characteristic portions thereof are described.

As shown in Fig. 11, since the intermediate plate 110 is disposed between the first cylinder 107a and the second cylinder 107b, the first injection hole 205a1 and the second injection hole 205a2 Each of a set of one common hole 205f1 and a set of the third jetting hole 205a3, the fourth jetting hole 205a4, and the second common hole 205f2 is formed in one intermediate plate 110. Since each injection hole and each common hole are formed in one intermediate plate 110, the injection flow path 205 can be formed with a simpler configuration.

<Effect of Embodiment 2>

According to the second embodiment, the first eccentric portion 104b and the second eccentric portion 104c, the first piston 105a and the second piston, and the first cylinder 107a and the second cylinder 107b are 2 There are dogs. The partition portion in which the injection hole with the common hole is formed is an intermediate plate 110 disposed between the two first cylinders 107a and the second cylinder 107b.

According to this configuration, the injection flow path 205 can be formed with a simpler configuration.

According to the second embodiment, the common hole formed in the intermediate plate 110 sprays the injection refrigerant into the first compression chamber 106a and the second compression chamber in the two first cylinders 107a and the second cylinder 107b. The plurality of first injection holes 205a1, the second injection holes 205a2, the third injection holes 205a3, and the fourth injection holes 205a4 are in common and communicated with each other.

According to this configuration, the number of processing steps is smaller, and the injection flow path 205 can be formed with a simpler configuration.

Embodiment 3

12 is an explanatory view showing a cross section in which the first injection hole 205a1 and the second injection hole 205a2 opened in the first compression chamber 106a according to the third embodiment of the present invention are visible. In the third embodiment, description of the same matters as in the above embodiment is omitted, and only the characteristic portions thereof are described.

As shown in Fig. 12, the inner diameter of the first cylinder 107a is 60 mm. The outer diameter of the first piston 105a is 44 mm. Two of the first injection hole 205a1 and the second injection hole 205a2 are provided. Both the first injection hole 205a1 and the second injection hole 205a2 have a hole diameter of 2 mm. The distance from the center of the first cylinder 107a to the center of each of the first and second injection holes 205a1 and 205a2 is 26 mm. The phase of the first injection hole 205a1 is 30° in the counterclockwise direction from the reference with the vane 105a1 at 0°. The phase of the second injection hole 205a2 is 330° in the counterclockwise direction from the reference with the vane 105a1 at 0°. The angle of the suction hole 107a2 through which the non-injection refrigerant flows is 30°. The hole diameter of the suction hole 107a2 is 10 mm. The length of the suction hole 107a2 through the first cylinder 107a is 20 mm. The injection refrigerant pressure Pinj is the intermediate pressure between the suction pressure Ps and the discharge pressure Pd. Ps=0.5 MPaG. Pd=4.0 MPaG. Pinj=1.5MPaG.

The opening section of the first injection hole 205a1 is -345° to -75°. That is, the first injection hole 205a1 is opened before 15°, which is a phase in which the first piston 105a passes through the suction hole 107a2 in order to form the first compression chamber 106a. In addition, although the phase at which the internal pressure of the first compression chamber 106a becomes higher than the injection refrigerant pressure differs depending on the operating conditions, the compression ratio, which is the ratio of the absolute pressure of the discharged refrigerant and the suction refrigerant, which is a heating operation condition of a general twin rotary compressor In this case, the internal pressure of the first compression chamber 106a becomes higher than the injection refrigerant pressure in the region where the rotation axis phase is 130° or more. The first injection hole 205a1 of the third embodiment is not opened in a region of a rotation axis phase of 130° or more in which the internal pressure of the first compression chamber 106a becomes higher than the injection refrigerant pressure. The first injection hole 205a1 communicates with the suction hole 107a2 in some sections.

The opening section of the second injection hole 205a2 is 75° to 345°. That is, the second injection hole 205a2 is opened after 15°, which is a phase in which the first piston 105a passes through the suction hole 107a2 in order to form the first compression chamber 106a. Further, it is opened in a region where the internal pressure of the first compression chamber 106a is higher than the injection refrigerant pressure. The second injection hole 205a2 does not always communicate with the suction hole 107a2 through which the refrigerant from the refrigeration cycle circuit of the first cylinder 107a is introduced into the first compression chamber 106a.

If the first injection hole 205a1 is opened before the phase forming the first compression chamber 106a, the injection refrigerant inhibits the suction of the refrigerant intake from the main circuit of the refrigeration cycle circuit, and the amount of refrigerant discharged decreases. Thereby, the heating capacity is lowered, and the injection effect becomes small. For this reason, it is desirable to avoid such a state. This is called constraint A.

In addition, when the second injection hole 205a2 is opened in a region where the internal pressure of the first compression chamber 106a is higher than the injection refrigerant pressure, the refrigerant in the first compression chamber 106a flows back into the injection flow path 205, The amount of discharged refrigerant decreases, the heating capacity decreases, and the injection effect decreases. For this reason, it is desirable to avoid such a state. This is called constraint B.

In order to improve the injection effect, it is preferable to achieve both the above restrictions A and B. However, for that reason, the position of the injection hole is close to the center of the first cylinder 107a, and the hole diameter of the injection hole needs to be reduced. In that case, the injection flow path 205 becomes narrow, and the injection effect falls.

In the third embodiment, all of the first injection holes 205a1 and the second injection holes 205a2 do not both satisfy the restrictions A and B, and one injection hole satisfies only the restriction on one side. Specifically, the opening section of the first injection hole 205a1 satisfies the restriction A but does not satisfy the restriction B. The opening section of the second injection hole 205a2 satisfies the constraint B but does not satisfy the constraint A. Accordingly, while the length of the opening section of the first spray hole 205a1 and the second spray hole 205a2 is maximized, the number of opening spray holes is selectively reduced in a section where the injection effect is lowered. Here, to maximize the length of the opening section of the injection hole is to bring the injection hole extremely close to the inner diameter wall surface of the first cylinder.

In addition, in the third embodiment, the opening sections of the two injection holes are not common. However, the opening section of the two injection holes may be made common. That is, the rotation angle at which the first piston 105a closes the suction hole 107a2 is set to α. The rotation angle at which the internal pressure of the first compression chamber 106a becomes higher than the injection refrigerant pressure is set to β. The opening section of the first injection hole 205a1 is set to θAs to θAe. The opening section of the second injection hole 205a2 is set to θBs to θBe. At this time, the relationship may be θAs<α<θBs<θAe<β<θBe. Thereby, the number of apertures of the two injection holes in a phase less than α or greater than β at which the injection effect is lowered is one. In addition, the number of apertures of the two injection holes in the phase of α or more and less than or equal to β in which the injection effect is not reduced is two. Therefore, the injection effect becomes higher.

<Effect of Embodiment 3>

According to the third embodiment, at least one of the plurality of first injection holes 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4 is the first compression. The internal pressure of the chamber 106a and the second compression chamber is always closed in a section higher than the injection pressure of the injection flow path 205. At least one other injection hole among the plurality of first injection holes 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4 is a first compression chamber 106a and The internal pressure of the second compression chamber is opened in a portion of the section higher than the injection pressure of the injection flow path 205.

According to this configuration, when the first injection hole 205a1 is opened before the phase forming the first compression chamber 106a, the injection refrigerant inhibits the suction of the suction refrigerant from the main circuit of the refrigeration cycle circuit, and is discharged. The amount of refrigerant decreases. Thereby, the heating capacity is lowered, and the injection effect becomes small. For this reason, it is preferable to avoid opening the first injection hole 205a1 before the phase forming the first compression chamber 106a. This is called constraint A. In addition, when the second injection hole 205a2 is opened in a region where the internal pressure of the first compression chamber 106a is higher than the injection refrigerant pressure, the refrigerant in the first compression chamber 106a flows back into the injection flow path 205, The amount of discharged refrigerant decreases, the heating capacity decreases, and the injection effect decreases. For this reason, it is preferable to avoid opening the second injection hole 205a2 in a region where the internal pressure of the first compression chamber 106a becomes higher than the injection refrigerant pressure. This is called constraint B. In the third embodiment, the opening section of one first injection hole 205a1 satisfies the restriction A, but does not satisfy the restriction B. Further, the opening section of the other second injection hole 205a2 satisfies the constraint B, but does not satisfy the constraint A. Accordingly, in a section in which the injection effect is lowered, the number of opening injection holes is selectively reduced. Therefore, it is possible to suppress a decrease in the injection effect. In addition, the relationship between the 1st injection hole 205a1 and the 2nd injection hole 205a2 is the same even if it is the relationship between the 3rd injection hole 205a3 and the 4th injection hole 205a4.

According to the third embodiment, at least one of the plurality of first injection holes 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4 is a first cylinder. (107a) and the refrigerant from the refrigeration cycle circuit of the second cylinder 107b do not always communicate with the suction hole 107a2 introduced into the first compression chamber 106a and the second compression chamber. At least one other injection hole among the plurality of first injection holes 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4 is a suction hole 107a2 in some sections. ) To communicate.

According to this configuration, regardless of the eccentric movement of the first piston 105a and the second piston, the injection effect is further enhanced by always opening any one of the injection holes completely.

Embodiment 4

Fig. 13 is an explanatory view showing a cross section in which the injection hole 205a opened in the first compression chamber 106a according to the fourth embodiment of the present invention is visible. In the fourth embodiment, description of the same matters as in the above embodiment is omitted, and only the characteristic portions thereof are described.

As shown in Fig. 13, three or more injection holes 205a may be used. For example, n injection holes 205a may be provided, or n-1 or less common holes 205f may be provided to communicate the n injection holes 205a. In Embodiment 4, there are three injection holes 205a. There are two common holes 205f. The phases of the three injection holes 205a are at respective positions of 270°, 225°, and 180° in the counterclockwise direction from the reference with the vane 105a1 being 0°. The two common holes 205f intersect. One end of one common hole 205f communicates with the upstream side in the injection coolant flow direction of the injection flow path 205 and the other end of one common hole 205f is closed. Both ends of the other common hole 205f are closed. One end of the remaining common hole 205f is open on the side surface of the upper bearing 109a for processing, and is thus covered with a cover member 109a1. One of the three injection holes 205a is formed at a position where the two common holes 205f intersect. Thereby, two injection holes 205a are formed in the two common holes 205f, respectively. One injection hole 205a formed at a position where the two common holes 205f intersect is in the vicinity of the connection part with the upstream side of the injection flow path 205, and in the section requiring the most injection refrigerant amount, more injection Refrigerant can be injected.

<Effect of Embodiment 4>

According to the fourth embodiment, the first common hole 205f1 and the second common hole 205f2 are plural with respect to the upper bearing 109a, the lower bearing 109b, and the intermediate plate 110. There are three or more injection holes per compression chamber. The plurality of first common holes 205f1 and second common holes 205f2 intersect.

According to this configuration, the injection flow path 205 can always communicate with the first compression chamber 106a and the second compression chamber.

According to the fourth embodiment, one end of one common hole among the plurality of common holes communicates with the upstream side in the injection coolant flow direction of the injection flow path 205 and the other end of the one common hole is closed. Both ends of the other common hole among the plurality of common holes are closed.

According to this configuration, only one common hole communicates with the upstream side in the injection refrigerant flow direction of the injection flow path 205. Thereby, the injection flow path 205 can be simplified, and the injection flow path 205 can be formed with a simple structure.

According to the fourth embodiment, at least one of the plurality of injection holes is formed at a position where the plurality of common holes intersect.

According to this configuration, more injection refrigerant can be injected in a section where the injection hole at the position where the plurality of common holes intersect requires the most injection refrigerant amount. Thereby, the injection effect becomes higher.

Further, Embodiments 1 to 4 of the present invention may be combined, or may be applied to other parts. In addition, in the said embodiment, the twin rotary compressor was mentioned as an example and demonstrated. However, the present invention may be applied to other rotary compressors such as a single rotary compressor.

100: twin rotary compressor 101: closed container
101a: cylindrical member 101b: upper block member
101c: lower blocking member 102: pedestal
103: electric motor 103a: stator
103b: rotor 104: crankshaft
104a: spindle 104b: first eccentric
104c: second eccentric portion 104d: auxiliary shaft
105a: first piston 105a1: vane
105a2: sliding surface 105a3: R processing
106a: first compression chamber 107a: first cylinder
107a1: through hole 107a2: suction hole
107a3: discharge hole 107b: second cylinder
108a: first inflow refrigerant pipe 108b: second inflow refrigerant pipe
109a: upper bearing 109a1: cover member
109b: lower bearing 110: middle plate
112: discharge pipe 113: suction muffler
200: refrigeration cycle device 201: condenser
202: expansion valve 203: evaporator
204: refrigerant pipe 205: injection flow path
205a: injection hole 205a1: first injection hole
205a2: second injection hole 205a3: third injection hole
205a4: fourth injection hole 205b: bypass tube
205c: first injection tube 205d: second injection tube
205e: injection muffler 205f: common hole
205f1: first common hole 205f2: second common hole
206: accumulator 207: separator
208: control valve

Claims (19)

An electric motor having a stator and a rotor,
A crankshaft that has an eccentric portion provided on a main shaft fixed to the rotor and rotates by the electric motor,
A piston provided in the eccentric portion,
A rotary compressor having a cylinder in which a cylindrical through hole is formed and the eccentric portion and the piston are disposed in the through hole to form a compression chamber,
An injection flow path for injecting an injection refrigerant into the compression chamber,
And a partition portion for closing the through hole in the cylinder,
The injection flow path has a plurality of injection holes for injecting an injection refrigerant into the compression chamber from within the partition, and a common hole formed in the partition and communicating with the plurality of injection holes.
Rotary compressor. The method of claim 1,
At least one of the plurality of injection holes is always open to the compression chamber.
Rotary compressor. The method according to claim 1 or 2,
The plurality of injection holes are formed at a position equidistant from the center of the cylinder
Rotary compressor. The method according to any one of claims 1 to 3,
The plurality of injection holes are formed adjacent to the inner diameter boundary of the cylinder
Rotary compressor. The method according to any one of claims 1 to 4,
A plurality of the injection holes are formed inscribed in the inner diameter boundary of the cylinder
Rotary compressor. The method according to any one of claims 1 to 5,
The common hole is formed by being inserted into the center of the cylinder than the tangent line of the inner diameter of the cylinder.
Rotary compressor. The method according to any one of claims 1 to 6,
All of the plurality of injection holes are formed on the outer diameter side of the sliding surface relative to the partition portion of the piston than the inner diameter boundary of the piston.
Rotary compressor. The method according to any one of claims 1 to 7,
At least one of the plurality of injection holes is always closed in a section in which the internal pressure of the compression chamber is higher than the injection pressure of the injection flow path,
At least another one of the plurality of injection holes is opened in a portion of a section in which the internal pressure of the compression chamber is higher than the injection pressure of the injection flow path.
Rotary compressor. The method according to any one of claims 1 to 8,
At least one of the plurality of injection holes does not always communicate with the suction hole of the cylinder,
At least another one of the plurality of injection holes communicates with the suction hole in a partial section.
Rotary compressor. The method according to any one of claims 1 to 9,
The common hole is a straight line
Rotary compressor. The method according to any one of claims 1 to 10,
The common hole is one with respect to the partition
Rotary compressor. The method according to any one of claims 1 to 10,
The common hole is plural with respect to the partition,
The injection holes are three or more for one compression chamber,
A plurality of said common holes intersecting
Rotary compressor. The method of claim 12,
One end of one of the common holes among the plurality of common holes communicates with an upstream side in the injection coolant flow direction of the injection flow path, and the other end of the one common hole is closed,
Both ends of the other common hole among the plurality of common holes are closed
Rotary compressor. The method of claim 12 or 13,
At least one of the plurality of injection holes is formed at a position where the plurality of common holes intersect.
Rotary compressor. The method according to any one of claims 1 to 14,
The partition portion in which the common hole and the plurality of injection holes are formed is a bearing covering an end face of the cylinder.
Rotary compressor. The method according to any one of claims 1 to 15,
The eccentric portion, the piston, and two cylinders are provided,
The partition portion in which the common hole and the plurality of injection holes are formed is an intermediate plate disposed between the two cylinders.
Rotary compressor. The method of claim 16,
The common hole formed in the intermediate plate is common and communicated with a plurality of the injection holes for injecting an injection refrigerant into the compression chamber in the two cylinders.
Rotary compressor. Comprising the rotary compressor according to any one of claims 1 to 17
Refrigeration cycle device. The method of claim 18,
Having a control valve for controlling the flow rate of the injection refrigerant in the middle of the injection flow path on the upstream side of the rotary compressor in the injection refrigerant flow direction
Refrigeration cycle device.

Images