JP7003272B2 - Rotary compressor and refrigeration cycle equipment - Google Patents

Description

The present invention relates to a rotary compressor and a refrigeration cycle device having a partition for closing a through hole in a cylinder.

In a conventional rotary compressor, an electric motor consisting of a rotor and a stator is mounted on the upper part of a closed container. Then, the rotation of the motor is transmitted downward by the crank shaft fixed to the rotor. A compression mechanism is configured below the crank shaft. The compression mechanism unit mainly includes a cylinder, a main bearing, an auxiliary bearing, an intermediate plate, and a piston. In the compression mechanism section, the rotation of the eccentric crank shaft causes the piston to move eccentrically, and the volume of the compression chamber is reduced, so that the refrigerant is compressed.

Further, in any one or more of the main bearing, the auxiliary bearing, and the intermediate plate, injection holes for introducing the injection refrigerant are 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 intake refrigerant from the main circuit of the refrigeration cycle circuit, the injection refrigerant from the injection flow path is injected into the compression chamber, so that the amount of discharge refrigerant increases and the flow rate of the refrigerant on the condenser side of the refrigeration cycle circuit increases. And the heating capacity is improved. Further, the reliability of the rotary compressor can be improved by cooling the sliding parts forming the compression mechanism portion by the injection refrigerant and appropriately maintaining the gap between the sliding parts.

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 Unexamined Patent Publication No. 2012-251485 Japanese Unexamined Patent Publication No. 2016-23582

In order to configure the injection flow path in the twin rotary compressor, it is necessary to form the injection flow path in the partition portion such as a bearing or an intermediate plate. In the bearing or intermediate plate inside the inner diameter of the cylinder, the piston that moves eccentrically passes through, so there is a section where the injection refrigerant does not completely flow. In the section where the injection refrigerant does not flow, the refrigerant that flows into the compression chamber is only the suction refrigerant from the main circuit of the refrigeration cycle circuit. Therefore, the amount of the discharged refrigerant is reduced, and the injection effect is reduced. Further, in the section where the injection refrigerant does not flow, the sliding parts are not cooled and the reliability cannot be improved.

The present invention is for solving the above-mentioned problems, and the injection refrigerant always flows into the compression chamber regardless of the eccentric movement of the piston, the amount of the discharged refrigerant increases, the injection effect is obtained, and the sliding parts are provided. It is an object of the present invention to provide a rotary compressor and a refrigerating cycle device which are constantly cooled and can improve reliability.

The rotary compressor according to the present invention has an electric motor having a stator and a rotor, a crank shaft having an eccentric portion provided on a main shaft fixed to the rotor, and being rotated by the electric motor, and the deviation. A rotary compressor provided with a piston provided in a core portion and a cylinder in which a cylindrical through hole is formed and the eccentric portion and the piston are arranged in the through hole to form a compression chamber. It is provided with 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, and the partition portion is a bearing covering the end face of the cylinder and the injection. The flow path has a plurality of injection holes formed in the bearing and injecting an injection refrigerant from the inside of the bearing into the compression chamber, and a common hole formed in the bearing and communicating with the plurality of injection holes. Then, one group of two or more holes among the plurality of injection holes communicates with one and the same common hole, and one group of two or more holes among the plurality of injection holes communicates with one and the same compression chamber. It is formed so as to inject an injection refrigerant into the bearing .

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

According to the rotary compressor and the refrigerating cycle apparatus according to the present invention, the injection flow path is formed in a plurality of injection holes for injecting an injection refrigerant from the inside of the partition portion into the compression chamber, and in the partition portion, and communicates with the plurality of injection holes. It has a common hole. As a result, the opening area in 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. Therefore, the injection refrigerant always flows into the compression chamber regardless of the eccentric movement of the piston, the amount of the discharged refrigerant increases, the injection effect is obtained, and the sliding parts are constantly cooled, so that the reliability can be improved.

It is a refrigerant circuit diagram which shows the refrigerating cycle apparatus which applied the twin rotary compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing which shows the vertical cross section of the twin rotary compressor which concerns on Embodiment 1 of this invention. It is a side view which shows the upper bearing which formed the common hole which concerns on Embodiment 1 of this invention. It is explanatory drawing which shows the cross section which can see the injection hole opened in the compression chamber which concerns on Embodiment 1 of this invention. It is explanatory drawing which shows the cross section of the upper bearing which formed the common hole and the injection hole which concerns on Embodiment 1 of this invention in the cross section AA of FIG. It is explanatory drawing which shows the vertical cross section of the piston which concerns on Embodiment 1 of this invention. It is explanatory drawing which shows the opening state of the injection hole corresponding to the eccentric movement of the piston which concerns on Embodiment 1 of this invention in the range of 0 ° to 360 °. It is explanatory drawing which shows the cross section which can see the injection hole opened in the compression chamber which concerns on the modification 1 in Embodiment 1 of this invention. It is explanatory drawing which shows the vertical cross section of the compression mechanism part of the twin rotary compressor which concerns on Embodiment 2 of this invention. It is explanatory drawing which shows the cross section of the intermediate plate which formed the common hole and the injection hole which concerns on Embodiment 2 of this invention. It is explanatory drawing which shows the cross section of the intermediate plate which formed the common hole and the injection hole which concerns on the modification 2 in Embodiment 2 of this invention. It is explanatory drawing which shows the cross section which can see the injection hole opened in the compression chamber which concerns on Embodiment 3 of this invention. It is explanatory drawing which shows the cross section which can see the injection hole opened in the compression chamber which concerns on Embodiment 4 of this invention.

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

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

As shown in FIG. 1, the refrigeration cycle device 200 includes a twin rotary compressor 100, a condenser 201, an expansion valve 202, and an evaporator 203. The twin rotary compressor 100, the condenser 201, the expansion valve 202, and the evaporator 203 are connected by a refrigerant pipe 204 to form a refrigeration cycle circuit. Then, the refrigerant flowing out of the evaporator 203 is sucked into the twin rotary compressor 100 via the accumulator 206 and becomes high temperature and high pressure. The high temperature and high pressure refrigerant is condensed in the condenser 201 to become a liquid. The liquid refrigerant is decompressed and expanded by the expansion valve 202 to become a low-temperature low-pressure gas-liquid two-phase, and the gas-liquid two-phase refrigerant is heat-exchanged in the evaporator 203.

The refrigerating cycle device 200 provides an injection flow path 205 for injecting refrigerant into the compression chamber from the separator 207 arranged in 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 refrigerating cycle circuit. Be prepared. A control valve 208 for controlling the flow rate of the injection refrigerant is provided in the middle of the injection flow path 205. The control valve 208 is arranged in the injection flow path 205 on the upstream side in the injection refrigerant flow direction with respect to the twin rotary compressor 100. The control valve 208 is composed of, for example, an on-off valve, a check valve, a flow rate adjusting valve, or the like, and adjusts the injection refrigerant flow rate so as to obtain an optimum injection effect. The 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. Examples of the refrigerating cycle device 200 include an air conditioner, a refrigerating device, a water heater, and the like.

<Structure of twin rotary compressor 100>
FIG. 2 is an explanatory view showing a vertical cross section of the twin rotary compressor 100 according to the first embodiment of the present invention. FIG. 3 is a side view showing the upper bearing 109a in which the first common hole 205f1 according to the first embodiment of the present invention is formed. FIG. 4 is an explanatory view showing a visible cross section of 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. FIG. 5 shows the cross section of the upper bearing 109a in which the first common hole 205f1 and the first injection hole 205a1 and the second injection hole 205a2 according to the first embodiment of the present invention are formed in the cross section AA of FIG. It is explanatory drawing which shows. FIG. 6 is an explanatory view showing a vertical cross 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 cylindrical closed container 101 whose upper and lower ends are closed. The closed container 101 has a tubular member 101a, a bowl-shaped upper end closing member 101b that closes the upper end portion of the tubular member 101a, and a bowl-shaped lower end closing member 101c that closes the lower end portion of the tubular member 101a. The closed container 101 is installed and fixed to the pedestal 102.

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

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

The spindle 104a is fixed to the rotor 103b. The spindle 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 main shaft 104a side above the second eccentric portion 104c, eccentrics the main shaft 104a and the center line, 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 auxiliary shaft 104d below the first eccentric portion 104b, eccentric the main shaft 104a and the first eccentric portion 104b and the center line, and is larger than the main shaft 104a. ..

As shown in FIG. 4, the first eccentric portion 104b is provided with a first piston 105a. The first piston 105a has a vane 105a1 that partitions the first compression chamber 106a. The first piston 105a is also called a rolling piston.

The first eccentric portion 104b and the first piston 105a are arranged in the first cylinder 107a in which the cylindrical through hole 107a1 is formed. In the first cylinder 107a, the first eccentric portion 104b and the first piston 105a are arranged in the through hole 107a1 to form the first compression chamber 106a. An upper bearing 109a and an intermediate plate 110 that partition the first compression chamber 106a in the vertical direction in the first cylinder 107a are arranged. 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 via a through hole 107a1.

Further, similarly to FIG. 4, the second eccentric portion 104c is provided with a second piston (not shown). The second piston has a vane that separates the second compression chamber. The second piston is also called a rolling piston.

The second eccentric portion 104c and the second piston are arranged below the first cylinder 107a in the second cylinder 107b in which a cylindrical through hole is formed. In the second cylinder 107b, a second eccentric portion 104c and a second piston are arranged 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 arranged. 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 via a through hole.

The upper bearing 109a that covers the upper end surface of the first cylinder 107a constitutes the upper wall portion of the first compression chamber 106a while slidably holding the crankshaft 104.

The lower bearing 109b that covers the lower end surface of the second cylinder 107b constitutes the lower wall portion of the second compression chamber while slidably holding the crankshaft 104.

The intermediate plate 110 arranged 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 forms the first compression chamber 106a and the first compression chamber 106a. It separates the two compression chambers.

Both the inflow inlets of the first inflow refrigerant pipe 108a and the second inflow refrigerant pipe 108b are inserted upward into the suction muffler 113. The suction muffler 113 is connected by inserting the refrigerant pipe 204 of the refrigerating cycle circuit downward and connected to allow the refrigerant to flow in. The suction muffler 113 is fixed to the outer periphery of the closed container 101.

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

An oil separator (not shown) is fitted in the upper part of the crank shaft 104. The oil separator prevents the refrigerating machine oil from leaving the machine through the discharge pipe 112 together with the discharged refrigerant. The oil separator blocks the flow path for the mixed fluid of the refrigerant and the refrigerating machine oil flowing toward the discharge pipe 112, collides and separates the refrigerant and the refrigerating machine oil, and suppresses the outflow of the refrigerating machine oil to the outside of the machine.

In the twin rotary compressor 100, the crank shaft 104 fixed to the rotor 103b of the motor portion is rotated by the electric motor 103. As a result, 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 portions of the first eccentric portion 104b and the second eccentric portion 104c, respectively, Eccentric rotation. Then, the volumes of the first compression chamber 106a and the second compression chamber separated by the vane 105a1 are reduced, and the refrigerant is compressed to change to a high pressure. The first compression chamber 106a and the second compression chamber are provided with a discharge valve that is released when the pressure exceeds a predetermined pressure. When the discharge valve is opened, a high-temperature and high-pressure gas refrigerant is discharged into the closed container 101. The compressed gas refrigerant passes through the discharge pipe 112 and is discharged into the refrigeration cycle circuit outside the twin rotary compressor. The operating refrigerant is, for example, R410A refrigerant.

<Details of injection flow path 205>
As shown in FIG. 1, the injection flow path 205 is the first compression chamber 106a from the separator 207 provided in 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. And the refrigerant is injected into each of the second compression chambers.

As shown in FIG. 2, the injection flow path 205 has a first injection hole 205a1, a second injection hole 205a2, a third injection hole 205a3, a fourth injection hole 205a4, a first common hole 205f1, and a second common hole. It has a hole 205f2, a bypass pipe 205b, a first injection pipe 205c, a second injection pipe 205d, and an injection muffler 205e.

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

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 inscribed in the inner diameter boundary of the first cylinder 107a. As a result, as will be described later, at least one of the first injection hole 205a1 and the second injection hole 205a2 always opens into the first compression chamber 106a.

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

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 third injection hole 205a3 and the fourth injection hole 205a4 are formed inscribed in the inner diameter boundary of the second cylinder 107b. As a result, at least one of the third injection hole 205a3 and the fourth injection hole 205a4 always opens into the second compression chamber, similarly to the first injection hole 205a1 and the second injection hole 205a2.

As shown in FIG. 4, the positions of the first injection hole 205a1 and the second injection hole 205a2, the hole diameters of the first injection hole 205a1 and the second injection hole 205a2, the outer diameter of the first piston 105a, and the first cylinder 107a. By appropriately setting the relationship between the inner diameters, at least one of the first injection hole 205a1 and the second injection hole 205a2 can always be opened. Here, the configuration inside the first cylinder will be described. The configuration inside the second cylinder is the same.

In the first embodiment, the inner diameter of the first cylinder 107a is 50 mm. The outer diameter of the first piston 105a is 32 mm. Two, a first injection hole 205a1 and a second injection hole 205a2 are provided. The hole diameters of the first injection hole 205a1 and the second injection hole 205a2 are both 4 mm. The distance from the center of the cylinder to the center of the holes of the first injection hole 205a1 and the second injection hole 205a2 is 22.9 mm. The phases of the first injection hole 205a1 and the second injection hole 205a2 are located at 270 ° and 180 ° counterclockwise with respect to the reference where the position of the vane 105a1 is 0 °.

As shown in FIG. 6, chamfered R processing 105a3 is applied to the inside of 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. All of the first injection hole 205a1 and the second injection hole 205a2 are formed on the outer diameter side of 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. As a result, the injection of the injection refrigerant from the first injection hole 205a1 and the second injection hole 205a2 into the central hole of the first piston 105a is prevented.

As shown in FIGS. 2, 3 and 5, the first common hole 205f1 is formed by hollowing a part of the upper bearing 109a as a partition portion into a linear horizontal hole. The first injection pipe 205c is connected to the opening on the side surface of the upper bearing 109a in the first common hole 205f1. 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 first common hole 205f1 is one for the first injection hole 205a1 and the second injection hole 205a2. The first common hole 205f1 is formed so as to enter the center side of the first cylinder 107a from the tangent line of the inner diameter of the first cylinder 107a.

The second common hole 205f2 is formed by hollowing a part of the lower bearing 109b as a partition portion into a linear horizontal hole. A second injection pipe 205d is connected to the opening on the side surface of the lower bearing 109b in the second common hole 205f2. The inner end of the second common hole 205f2 is closed and closed. The second common hole 205f2 communicates 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 so as to enter the center side of the second cylinder 107b from the 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 the tip downward.

The first injection pipe 205c has an inlet inserted upward into the injection muffler 205e, is connected to the first common hole 205f1, and supplies the refrigerant to the first injection hole 205a1 and the second injection hole 205a2.

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

The injection muffler 205e is arranged between the bypass 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. As a result, 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 205e is fixed to the outer peripheral portion of the closed 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 injection flow path 205>
FIG. 7 is an explanatory view showing the opening states of the first injection hole 205a1 and the second injection hole 205a2 in the range of 0 ° to 360 ° according to the eccentric movement of the first piston 105a according to the first embodiment of the present invention. Is. Here, the operating state of the first piston 105a will be described. The same applies to the second piston.

First, when the first piston 105a is located at 0 ° to 135 ° counterclockwise based on the reference where the position of the vane 105a1 is 0 °, both the first injection hole 205a1 and the second injection hole 205a2 It is also open. Therefore, the injection refrigerant flows into the first compression chamber 106a from both the first injection hole 205a1 and the second injection hole 205a2.

Next, when the first piston 105a is located at 135 ° to 225 ° counterclockwise based on the reference where the position of the vane 105a1 is 0 °, the first injection hole 205a1 slides on the first piston 105a. It is covered with the surface 105a2 and closed. The second injection hole 205a2 is maintained in an open state. Therefore, the injection refrigerant flows into the first compression chamber 106a only from the second injection hole 205a2.

When the first piston 105a is located at 225 ° to 315 ° counterclockwise based on the reference where the position of the vane 105a1 is 0 °, the second injection hole 205a2 is the sliding surface of the first piston 105a. It is covered with 105a2 and blocked. The closed first compression chamber 106a gradually narrows, and when a predetermined pressure is exceeded, the first compression chamber 106a is discharged as a high-temperature and high-pressure gas refrigerant from the discharge hole 107a3. On the other hand, the first injection hole 205a1 is opened in the next first compression chamber 106a, and the injection refrigerant flows into the first injection hole 205a1. As a result, regardless of the eccentric movement of the first piston 105a, either the first injection hole 205a1 or the second injection hole 205a2 opens 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 pipe 205c and the second injection pipe 205d in the injection muffler 205e, respectively. The refrigerant supplied to the first injection pipe 205c is a liquid or gas refrigerant from the first injection hole 205a1 and the second injection hole 205a2 to the inside of the first compression chamber 106a via the first common hole 205f1 of the twin rotary compressor 100. Is injected as. The refrigerant supplied to the second injection pipe 205d passes through the second common hole 205f2 of the twin rotary compressor 100, and is used as a liquid or gas refrigerant from the third injection hole 205a3 and the fourth injection hole 205a4 into the inside of the second compression chamber. Be injected.

At this time, the pressure in the injection muffler 205e is the injection pressure from the refrigeration cycle circuit and the pressures of the first injection pipe 205c and the second injection pipe 205d supplied to the first compression chamber 106a and the second compression chamber. It has an intermediate pressure. Therefore, it is difficult for the refrigerant to leak due to the differential pressure between the first compression chamber 106a and the second compression chamber.

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

<Effect of 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. Therefore, there is a phase in which the flow of the injection refrigerant is stopped. If the injection hole exists only at 270 °, the injection hole opens 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 portion, so that the injection effect cannot be expected.

On the other hand, in the first embodiment, one of the two first injection holes 205a1 and the second injection hole 205a2 is always open to the first compression chamber 106a. As a result, the flow of the injection refrigerant is not obstructed, and the injection effect is enhanced. Further, as the opening of the first injection hole 205a1 and the second injection hole 205a2, a complete opening is desirable. By always completely opening either the first injection hole 205a1 or the second injection hole 205a2, the injection effect is further enhanced. This also applies to the relationship between the third injection hole 205a3 and the fourth injection hole 205a4.

Further, by appropriately arranging the distance between the two first injection holes 205a1 and the second injection hole 205a2, the pulsation of the refrigerant flowing back from the first injection hole 205a1 and the second injection hole 205a2 is reflected by the first piston 105a. Therefore, the leakage of the refrigerant from the first compression chamber 106a to the suction chamber can be suppressed. This also applies to 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 long opening section of one injection hole increases the flow rate of the injection refrigerant and enhances the injection effect. Be done. Geometrically, to lengthen the opening section, the injection hole should be as far from the center of the cylinder as possible. However, if it is arranged outside the inner diameter of the cylinder, the injection flow path 205 is blocked by the inner diameter wall surface of the cylinder, and the injection effect is reduced. Further, if the formation of the inner diameter of the cylinder and the corner of the bearing end face is hindered by the injection hole, the sealing property due to the corner of the piston deteriorates, and the compressor efficiency decreases. It is preferable to arrange the position where the outer circumference of the injection hole is most inscribed from the inner diameter of the cylinder by about 0.1 mm to 3 mm inside.

When arranging a plurality of injection holes as far from the center of the cylinder as possible, it is preferable that the distances of the injection holes from the center of the cylinder are substantially the same. Further, it is preferable that the common hole in which the two injection holes are communicated is a straight line arranged so as to be displaced from the inner diameter tangent of the cylinder to the center side of the cylinder. As a result, the common hole allows the two injection holes to communicate with each other with a simple structure. Both the first common hole 205f1 and the second common hole 205f2 in the first embodiment are linear shapes arranged so as to be offset from the inner diameter of the cylinder toward the center side of the cylinder, and the distance from the center of the cylinder is 16. It is 2 mm.

By appropriately selecting the inner diameter and the amount of chamfering of the inner diameter of the piston, the injection hole and the central hole in the piston are always in a non-communication relationship. As a result, the inflow of the 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 the first embodiment, the inner diameter of the piston is 22 mm with respect to the outer diameter of 32 mm. The inner diameter chamfered amount of the piston is 0.5 mm in the radial direction and 0.2 mm in the height direction. By making the chamfering amount larger in the height direction than in the radial direction, the inflow of the high-pressure refrigerant into the injection flow path 205 can be further suppressed.

As described above, 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 of the injection refrigerant opening into the compression chamber is increased. , A larger flow rate of injection refrigerant can flow into the compression chamber. Further, only one injection pipe is inserted into the compression chamber from the outside of the closed container 101 for each compression chamber. In the first embodiment, one compression chamber is provided with a plurality of injection holes, but it is not necessary to provide a plurality of injection pipes. As a result, the degree of freedom in designing the outside of the closed container and the periphery of the compression mechanism can be improved.

The intersections of the injection holes and the common holes such as the first injection hole 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4 are arranged inside the inner diameter of the cylinder. At this intersection, one injection hole and one common hole are formed so as to intersect in a T shape. The hole corresponding to the vertical side of the T-shape may be either an injection hole or a common hole. However, of at least two injection holes, the one closer to the entrance of the common hole corresponds to the hole on the vertical side of the T-shape. In the first embodiment, 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, oval. When the injection hole is oval, it is desirable to arrange the major axis side in the tangential direction of the inner diameter of the cylinder in order to secure the communication section. In the first embodiment, the injection hole is circular.

The diameters of the plurality of injection holes may not be the same. Due to the large diameter of one of the injection holes, the distribution of the injection refrigerant in the compression chamber can be selectively changed. For example, the large diameter of the injection holes arranged in the phase closer to the vane 105a1 increases the amount of the injection refrigerant for cooling the vane 105a1, suppresses the thermal expansion of the vane 105a1, and provides a highly reliable twin rotary compressor 100. can.

<Modification 1>
FIG. 8 is an explanatory view showing a visible cross section of the first injection hole 205a1 and the second injection hole 205a2 opened in the first compression chamber 106a according to the first modification of the first embodiment of the present invention. In the first modification, the description of the same matters as in the above embodiment will be omitted, and only the characteristic portion thereof will be described.

As shown in FIG. 2, the injection refrigerant passes through the first injection pipe 205c and flows into the upper bearing 109a. 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 = 1.5 MPaG. As shown in FIG. 8, the injection refrigerant flowing into the first cylinder 107a passes through the first common hole 205f1 and is injected from the first injection hole 205a1 and the second injection hole 205a2 into the first compression chamber 106a. Here, the first injection hole 205a1 and the second injection hole 205a2 are arranged inside the inner diameter of the first cylinder 107a. In the first modification, 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 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 is arranged in a phase of 270 °, which is the revolution direction of the first piston 105a counterclockwise, with the vane 105a1 as a reference of 0 °. Further, the hole diameter of the second injection hole 205a2 is 3 mm, and the second injection hole 205a2 is arranged in a phase of 280 °. The injection refrigerant increases the mass of the refrigerant discharged from the twin rotary compressor 100, and improves the heating capacity of the refrigeration cycle device 200. Further, since the injection refrigerant has a lower temperature than the discharge refrigerant, the sliding parts, for example, the vane 105a1 are cooled to suppress thermal expansion, and 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 spindle 104a fixed to a rotor 103b, and includes a crank shaft 104 rotated by an electric motor 103. The twin rotary compressor 100 includes a first piston 105a and a second piston provided in the first eccentric portion 104b and the second eccentric portion 104c. In the twin rotary compressor 100, a cylindrical through hole 107a1 is formed, and a first eccentric portion 104b or a second eccentric portion 104c and a first piston 105a or a second piston are arranged in the through hole 107a1. A first cylinder 107a and a second cylinder 107b in which a compression chamber 106a or a second compression chamber is formed are provided. The twin rotary compressor 100 includes an injection flow path 205 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. The twin rotary compressor 100 includes an upper bearing 109a, a lower bearing 109b, and an intermediate plate 110 as a partition for closing the through hole in the first cylinder 107a or the second cylinder. The injection flow path 205 has a plurality of first injection holes 205a1, second injection holes 205a2, and a second injection hole 205a1 for injecting an injection refrigerant from the upper bearing 109a, the lower bearing 109b, or the intermediate plate 110 into the first compression chamber 106a or the second compression chamber. 3 Injection holes 205a3 and 4th injection holes 205a4, and a plurality of first injection holes 205a1, second injection holes 205a2, third injection holes 205a3 and fourth, which are formed in the upper bearing 109a, the lower bearing 109b or the intermediate plate 110. It has a first common hole 205f1 and a second common hole 205f2 that communicate with the injection hole 205a4.

According to this configuration, the opening area in which the injection refrigerant is injected into the first compression chamber 106a and the second compression chamber is increased by a simple configuration. Further, 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 movement of the first piston 105a and the second piston, the amount of the discharged refrigerant increases, the injection effect is obtained, and the sliding Parts can be constantly cooled to 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 the first compression chamber 106a and the first injection hole. 2 Open to the 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 hole 205a2, the third injection hole 205a3 and the fourth injection hole 205a4 are equidistant from the center of the first cylinder 107a and the second cylinder 107b. It is formed in a position.

According to this configuration, the opening section of one injection hole becomes long, the injection flow rate increases, and the injection effect is further enhanced.

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

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

According to the first embodiment, the plurality of first injection holes 205a1, the second injection hole 205a2, the third injection hole 205a3 and the fourth injection hole 205a4 are inscribed in the inner diameter boundary of the first cylinder 107a and the second cylinder 107b. Is formed.

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

According to the first embodiment, the first common hole 205f1 and the second common hole 205f2 enter the center side of the first cylinder 107a and the second cylinder 107b from the tangent of the inner diameters of the first cylinder 107a and the second cylinder 107b. Is formed of.

According to this configuration, the first common hole 205f1 and the second common hole 205f2 can communicate a 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 hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4 are the first piston 105a and the upper bearing 109a of the second piston. The sliding surface 105a2 with respect to the lower bearing 109b and the intermediate plate 110 is formed on the outer diameter side of the inner diameter boundary of the first piston 105a and the second piston.

According to this configuration, the injection refrigerant does not leak into the central 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. The first common hole 205f1 and the second common hole 205f2 do not have to be linear. For example, the first common hole 205f1 and the second common hole 205f2 may be curved, linear or meandering with a bent portion in the middle.

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 processing man-hours are small, the 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 the upper bearing 109a or the lower bearing 109b that covers the end face of the first cylinder 107a or the second cylinder 107b.

According to this configuration, the opening area in which the injection refrigerant is injected into the first compression chamber 106a and the second compression chamber is increased by a simple configuration. Further, 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 refrigerating cycle apparatus 200 provided with the twin rotary compressor 100, the injection refrigerant always flows into the first compression chamber 106a and the second compression chamber regardless of the eccentric movement of the first piston 105a and the second piston. However, the amount of discharged refrigerant is increased to obtain an injection effect, and the sliding parts are constantly cooled to improve reliability.

According to the first embodiment, the refrigerating cycle apparatus 200 has a control valve 208 for controlling 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 injection refrigerant flow direction.

According to this configuration, the control valve 208 adjusts the flow rate of the injection refrigerant, and the optimum injection effect can be obtained.

Embodiment 2.
FIG. 9 is an explanatory diagram showing a vertical cross section of the compression mechanism portion of the twin rotary compressor 100 according to the second embodiment of the present invention. FIG. 10 shows an intermediate plate 110 in which 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 are formed. It is explanatory drawing which shows the cross section of. In the second embodiment, the description of the same items as those in the above embodiment will be omitted, and only the characteristic portions thereof will be described.

As shown in FIGS. 9 and 10, the injection flow path 205 may be provided on the intermediate plate 110. That is, one first common hole 205f1, a first injection hole 205a1, a second injection hole 205a2, a third injection hole 205a3, and a fourth injection hole 205a4 are configured in the intermediate plate 110 as a partition portion. Since the intermediate plate 110 is arranged between the first cylinder 107a and the second cylinder 107b, the pair of the first injection hole 205a1 and the second injection hole 205a2 and the third injection hole 205a3 and the fourth injection hole 205a4 The pair is communicated with one first common hole 205f1. Further, by forming the intersection of the first common hole 205f1 and each injection hole in the shape of a cross, the injection flow path 205 can be formed with a simpler structure. In the second embodiment, all the intersections are configured in the shape of a cross.

<Modification 2>
FIG. 11 shows the first common hole 205f1, the second common hole 205f2, the first injection hole 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection according to the second modification of the second embodiment of the present invention. It is explanatory drawing which shows the cross section of the intermediate plate 110 which formed the hole 205a4. In the second modification, the description of the same matters as in the above embodiment will be omitted, and only the characteristic portion thereof will be described.

As shown in FIG. 11, since the intermediate plate 110 is arranged between the first cylinder 107a and the second cylinder 107b, the first injection hole 205a1, the second injection hole 205a2, and the first common hole 205f1 Each of the set and the set of the third injection hole 205a3, the fourth injection hole 205a4, and the second common hole 205f2 is configured in one intermediate plate 110. Since each injection hole and each common hole are configured 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 provided. ing. The partition portion in which the common hole and the injection hole are formed is an intermediate plate 110 arranged 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 is a plurality of injection refrigerants that inject the injection refrigerant into the first compression chamber 106a and the second compression chamber in the two first cylinder 107a and the second cylinder 107b. It communicates in common with the first injection hole 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4.

According to this configuration, the injection flow path 205 can be formed with a simpler configuration with less processing man-hours.

Embodiment 3.
FIG. 12 is an explanatory view showing a visible cross section of 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. In the third embodiment, the description of the same items as those in the above embodiment will be omitted, and only the characteristic portions thereof will be 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, a first injection hole 205a1 and a second injection hole 205a2 are provided. The hole diameters of the first injection hole 205a1 and the second injection hole 205a2 are both 2 mm. The distance from the center of the first cylinder 107a to the center of each of the first injection hole 205a1 and the second injection hole 205a2 is 26 mm. The phase of the first injection hole 205a1 is 30 ° counterclockwise with respect to the vane 105a1 as 0 °. The phase of the second injection hole 205a2 is 330 ° counterclockwise with respect to the vane 105a1 as 0 °. The angle of the suction hole 107a2 into 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 penetrating the first cylinder 107a is 20 mm. 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 = 1.5 MPaG.

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 the phase in which the first piston 105a passes through the suction hole 107a2 in order to form the first compression chamber 106a. Further, the phase in which the internal pressure of the first compression chamber 106a becomes higher than the injection refrigerant pressure differs depending on the operating conditions, but it depends on the ratio of the absolute pressure of the discharged refrigerant and the sucked refrigerant, which is the heating operating condition of a general twin rotary compressor. When a certain compression ratio is 6 to 12, 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 does not open in the region where the internal pressure of the first compression chamber 106a is higher than the injection refrigerant pressure and the rotation axis phase is 130 ° or more. The first injection hole 205a1 communicates with the suction hole 107a2 in a part of the section.

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 the phase in which the first piston 105a passes through the suction hole 107a2 in order to form the first compression chamber 106a. Further, the first compression chamber 106a is open in a region where the internal pressure is higher than the injection refrigerant pressure. The second injection hole 205a2 does not always communicate with the suction hole 107a2 that introduces the refrigerant from the refrigeration cycle circuit of the first cylinder 107a into the first compression chamber 106a.

When the first injection hole 205a1 is opened before the phase forming the first compression chamber 106a, the injection refrigerant hinders the suction of the intake refrigerant from the main circuit of the refrigeration cycle circuit, and the amount of the discharged refrigerant decreases. do. As a result, the heating capacity is reduced and the injection effect is reduced. Therefore, it is desirable to avoid such a situation. This is called constraint A.

Further, when the second injection hole 205a2 is opened in the 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, and the amount of the discharged refrigerant is discharged. Is reduced, the heating capacity is reduced, and the injection effect is reduced. Therefore, it is desirable to avoid such a situation. This is called constraint B.

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

In the third embodiment, not all the first injection holes 205a1 and the second injection holes 205a2 satisfy the above constraints A and B, and one injection hole satisfies only one constraint. Specifically, the opening section of the first injection hole 205a1 satisfies the constraint A but does not satisfy the constraint B. The opening section of the second injection hole 205a2 satisfies the constraint B but does not satisfy the constraint A. As a result, the number of injection holes to be opened can be selectively reduced in the section where the injection effect is reduced while the opening section length of the first injection hole 205a1 and the second injection hole 205a2 is maximized. Here, maximizing the opening section length of the injection hole means making the injection hole as close as possible to the inner diameter wall surface of the first cylinder.

In the third embodiment, the opening sections of the two injection holes are not common. However, the opening sections of the two injection holes may be shared. That is, the rotation angle at which the first piston 105a closes the suction hole 107a2 is set to α. Let β be the rotation angle at which the internal pressure of the first compression chamber 106a becomes higher than the injection refrigerant pressure. 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 such that θAs <α <θBs <θAe <β <θBe. As a result, the numerical aperture of the two injection holes in the phase less than α or larger than β at which the injection effect is reduced becomes one. Further, the numerical aperture of the two injection holes in the phase of α or more and β or less at which the injection effect does not decrease is two. Therefore, the injection effect is further enhanced.

<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 has the first compression chamber 106a and the second injection hole. The internal pressure of the compression chamber is always blocked in a section higher than the injection pressure of the injection flow path 205. 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 injected with the internal pressure of the first compression chamber 106a and the second compression chamber. It opens in a part of the section higher than the injection pressure of the 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 hinders the suction of the intake refrigerant from the main circuit of the refrigeration cycle circuit. The amount of discharged refrigerant decreases. As a result, the heating capacity is reduced and the injection effect is reduced. Therefore, it is desirable to avoid opening the first injection hole 205a1 before the phase forming the first compression chamber 106a. This is called constraint A. Further, when the second injection hole 205a2 is opened in the region where the internal pressure of the first compression chamber 106a is higher than the injection refrigerant pressure, the refrigerant of the first compression chamber 106a flows back into the injection flow path 205, and the amount of the discharged refrigerant is discharged. Is reduced, the heating capacity is reduced, and the injection effect is reduced. Therefore, it is desirable to avoid opening the second injection hole 205a2 in a region where the internal pressure of the first compression chamber 106a is 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 constraint A, but does not satisfy the constraint B. Further, the opening section of the other second injection hole 205a2 satisfies the constraint B, but does not satisfy the constraint A. As a result, the number of injection holes to be opened can be selectively reduced in the section where the injection effect is reduced. Therefore, the decrease in the injection effect can be suppressed. The relationship between the first injection hole 205a1 and the second injection hole 205a2 is the same as the relationship between the third injection hole 205a3 and the fourth 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 has the first cylinder 107a and the second cylinder. The refrigerant from the refrigeration cycle circuit of 107b does not always communicate with the suction holes 107a2 that are introduced into the first compression chamber 106a and the second compression chamber. 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 communicates with the suction hole 107a2 in a part of the section.

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

Embodiment 4.
FIG. 13 is an explanatory view showing a visible cross section of the injection hole 205a opened in the first compression chamber 106a according to the fourth embodiment of the present invention. In the fourth embodiment, the description of the same items as those in the above embodiment will be omitted, and only the characteristic portions thereof will be described.

As shown in FIG. 13, the number of injection holes 205a may be three or more. For example, n injection holes 205a may be provided, or n-1 or less common holes 205f may be provided in order to communicate the n injection holes 205a. In the fourth embodiment, there are three injection holes 205a. There are two common holes 205f. The phases of the three injection holes 205a are located at 270 °, 225 ° and 180 °, respectively, counterclockwise with respect to the vane 105a1 as 0 °. The two common holes 205f intersect. One end of the common hole 205f communicates with the upstream side in the injection refrigerant flow direction of the injection flow path 205, and the other end of the one common hole 205f is closed. Both ends of the remaining other common holes 205f are closed. Since one end of the remaining other common hole 205f is opened on the side surface of the upper bearing 109a due to processing, it is covered with the lid member 109a1. One of the three injection holes 205a is formed at a position where the two common holes 205f intersect. As a result, two injection holes 205a are formed in each of the two common holes 205f. One injection hole 205a formed at the intersection of the two common holes 205f is near the connection portion with the upstream side of the injection flow path 205, and more injection is performed in the section requiring the most injection refrigerant amount. 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 a plurality of the upper bearing 109a, the lower bearing 109b, and the intermediate plate 110. There are three or more injection holes for one 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 the common hole among the plurality of common holes communicates with the upstream side in the injection refrigerant flow direction of the injection flow path 205, and the other end of the one common hole is formed. It is blocked. Both ends of the other common holes among the plurality of common holes are closed.

According to this configuration, only one common hole communicates upstream in the injection refrigerant flow direction of the injection flow path 205. As a result, 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 injection hole of the plurality of injection holes is formed at a position where the plurality of common holes intersect.

According to this configuration, a larger amount of the injection refrigerant can be injected in the section where the injection hole at the position where the plurality of common holes intersects requires the most injection refrigerant amount. As a result, the injection effect is further enhanced.

In addition, the first to fourth embodiments of the present invention may be combined, or may be applied to other parts. Further, in the above embodiment, the twin rotary compressor has been described as an example. However, the present invention may be applied to other rotary compressors such as single rotary compressors.

100 Twin rotary compressor, 101 closed container, 101a tubular member, 101b upper end closing member, 101c lower end closing member, 102 pedestal, 103 electric motor, 103a stator, 103b rotor, 104 crank shaft, 104a spindle, 104b first deviation Core part, 104c 2nd eccentric part, 104d auxiliary shaft, 105a 1st piston, 105a1 vane, 105a2 sliding surface, 105a3 R processing, 106a 1st compression chamber, 107a 1st cylinder, 107a1 through hole, 107a2 suction hole, 107a3 Discharge hole, 107b 2nd cylinder, 108a 1st inflow refrigerant pipe, 108b 2nd inflow refrigerant pipe, 109a upper bearing, 109a1 lid member, 109b lower bearing, 110 intermediate plate, 112 discharge pipe, 113 suction muffler, 200 refrigeration cycle Equipment, 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 pipe, 205c 1st injection pipe, 205d 2nd injection pipe, 205e injection muffler, 205f common hole, 205f1 1st common hole, 205f2 2nd common hole, 206 accumulator, 207 separator, 208 control valve.

Claims (18)

Motors with stators and rotors,
A crank shaft having an eccentric portion provided on a spindle fixed to the rotor and rotated by the motor, and a crank shaft.
The piston provided in the eccentric portion and
A cylinder in which a cylindrical through hole is formed, and the eccentric portion and the piston are arranged in the through hole to form a compression chamber.
It is a rotary compressor equipped with
An injection flow path for injecting an injection refrigerant into the compression chamber,
A partition portion that closes the through hole in the cylinder,
Equipped with
The partition portion is a bearing that covers the end face of the cylinder.
The injection flow path includes a plurality of injection holes formed in the bearing and injecting an injection refrigerant from the inside of the bearing into the compression chamber, and a common hole formed in the bearing and communicating with the plurality of injection holes. Have,
A group of two or more of the plurality of injection holes communicates with one and the same common hole.
A group of two or more holes among the plurality of injection holes is a rotary compressor formed so as to inject an injection refrigerant into one and the same compression chamber . Motors with stators and rotors,
A crank shaft having an eccentric portion provided on a spindle fixed to the rotor and rotated by the motor, and a crank shaft.
The piston provided in the eccentric portion and
A cylinder in which a cylindrical through hole is formed, and the eccentric portion and the piston are arranged in the through hole to form a compression chamber.
It is a rotary compressor equipped with
An injection flow path for injecting an injection refrigerant into the compression chamber,
A partition portion that closes the through hole in the cylinder,
Equipped with
The eccentric portion, the piston, and the cylinder are provided in two.
The partition is an intermediate plate arranged between the two cylinders.
The injection flow path is formed in the intermediate plate and has a plurality of injection holes for injecting an injection refrigerant from the inside of the intermediate plate into the compression chamber, and a common injection hole formed in the intermediate plate and communicating with the plurality of injection holes. With a hole,
A group of two or more of the plurality of injection holes communicates with one and the same common hole.
A group of two or more holes among the plurality of injection holes is a rotary compressor formed so as to inject an injection refrigerant into one and the same compression chamber. The rotary compressor according to claim 1 or 2 , wherein at least one of the plurality of injection holes is always open to the compression chamber. The rotary compressor according to any one of claims 1 to 3 , wherein the plurality of injection holes are formed at positions equidistant from the center of the cylinder. The rotary compressor according to any one of claims 1 to 4 , wherein the plurality of injection holes are formed adjacent to an inner diameter boundary of the cylinder. The rotary compressor according to any one of claims 1 to 5 , wherein the plurality of injection holes are formed inscribed in the inner diameter boundary of the cylinder. The rotary compressor according to any one of claims 1 to 6 , wherein the common hole is formed by entering the center side of the cylinder from the tangent line of the inner diameter of the cylinder. The rotary compressor according to any one of claims 1 to 7 , wherein all of the plurality of injection holes are formed on the outer diameter side of the inner diameter boundary of the piston on the sliding surface of the piston with respect to the partition portion. .. At least one of the plurality of injection holes is always closed in a section where the internal pressure of the compression chamber is higher than the injection pressure of the injection flow path.
One of claims 1 to 8 , wherein at least one of the injection holes is opened in a part of a section where the internal pressure of the compression chamber is higher than the injection pressure of the injection flow path. The rotary compressor described in. At least one of the plurality of injection holes does not always communicate with the suction hole of the cylinder.
The rotary compressor according to any one of claims 1 to 9 , wherein at least one other injection hole among the plurality of injection holes communicates with the suction hole in a part of the section. The rotary compressor according to any one of claims 1 to 10 , wherein the common hole is linear. The rotary compressor according to any one of claims 1 to 11 , wherein the common hole is one for the partition portion. The common hole is a plurality with respect to the partition portion, and is
The number of injection holes is three or more for one compression chamber, and the number of injection holes is three or more.
The rotary compressor according to any one of claims 1 to 11 , wherein the plurality of common holes intersect. One end of the common hole among the plurality of common holes communicates upstream in the injection refrigerant flow direction of the injection flow path, and the other end of the common hole is closed.
The rotary compressor according to claim 13 , wherein both ends of the other common hole among the plurality of common holes are closed. The rotary compressor according to claim 13 , wherein at least one of the plurality of injection holes is formed at a position where the plurality of common holes intersect. The common hole formed in the intermediate plate is dependent on claim 2 or claim 2 which communicates in common with a plurality of the injection holes for injecting the injection refrigerant into the compression chambers in the two cylinders. The rotary compressor according to any one of 3 to 15 . A refrigeration cycle apparatus comprising the rotary compressor according to any one of claims 1 to 16 . The refrigerating cycle apparatus according to claim 17 , further comprising 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.

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