WO2023152799A1

WO2023152799A1 - Compressor and refrigeration cycle device with said compressor

Info

Publication number: WO2023152799A1
Application number: PCT/JP2022/004910
Authority: WO
Inventors: 亮濱田
Original assignee: 三菱電機株式会社
Priority date: 2022-02-08
Filing date: 2022-02-08
Publication date: 2023-08-17

Abstract

This compressor is provided with a closed container, an electric motor unit, a crankshaft, and a compression mechanism unit. The crankshaft has an eccentric shaft part. The compression mechanism unit comprises: a cylinder having a cylinder chamber into which a refrigerant is suctioned and compressed; a rolling piston that is fitted with the eccentric shaft part and is accommodated in the cylinder chamber, and that rotates with the eccentric shaft part to compress the refrigerant; and a vane that is provided in a vane groove formed in a radial direction of the cylinder and that follows the rolling piston to thereby partition the cylinder chamber into a suction chamber and a compression chamber for the refrigerant. The vane groove does not penetrate through to the outer peripheral surface of the cylinder on one end surface side of the cylinder. A vane stop part is formed at an end on the outer peripheral surface side of the cylinder. On the other end surface side of the cylinder, the vane groove is formed to penetrate through the outer peripheral surface of the cylinder. The vane is so configured that the length of a portion thereof positioned on the other end surface side of the cylinder on which the outer peripheral surface is penetrated through is longer than the length of a portion thereof positioned on the one end surface side of the cylinder at which the vane stop part is formed.

Description

Compressor and refrigeration cycle device provided with the compressor

The present disclosure relates to a compressor and a refrigeration cycle device provided with the compressor.

Conventionally, there is known a configuration including a sealed container, an electric motor section, a rotating shaft, and a compression mechanism section, such as the compressor disclosed in Patent Document 1, for example. The compression mechanism includes a cylinder having a cylinder chamber, a rolling piston that is accommodated in the cylinder chamber by being fitted to the eccentric shaft portion of the rotating shaft, rotates together with the eccentric shaft portion to compress the refrigerant, and is formed in the radial direction of the cylinder. and a vane provided in the vane groove formed in the cylinder and following the rolling piston to divide the cylinder chamber into a refrigerant suction chamber and a compression chamber.

In recent years, low GWP (Global Warming Potential) refrigerants such as R32, R1234yf or R290 have been used as refrigerants in refrigeration cycle devices equipped with compressors as one of the measures against global warming. However, low GWP refrigerants have a smaller refrigerating capacity per volume than conventionally used refrigerants such as R410A. Therefore, in the refrigerating cycle device, it is necessary to increase the flow rate of the refrigerant flowing inside in order to achieve the desired refrigerating capacity. Increasing the stroke volume of the compression chamber is effective in increasing the flow rate of the refrigerant. The stroke volume is the amount of refrigerant discharged per rotation of the compression mechanism. In order to increase this stroke volume, it is desirable to increase the inner diameter of the cylinder chamber.

WO2018/87955

However, in the conventional compressor disclosed in Patent Document 1, if the inner diameter of the cylinder chamber is increased, the amount of protrusion of the vane that protrudes into the cylinder chamber increases. If the amount of protrusion into the cylinder chamber is large relative to the total length of the vane, the operation becomes unstable, and the ability to follow the rolling piston deteriorates. As a result, the compressor may leak refrigerant from the high-pressure chamber to the low-pressure chamber in the cylinder chamber, and the compression efficiency may decrease. In addition, since the side area of the vane that supports the load of the refrigerant differential pressure applied from the high pressure chamber to the low pressure chamber becomes smaller, severe sliding conditions are created, causing seizure and failure of the compressor.

The present disclosure has been made in order to solve the above-described problems. It is an object of the present invention to provide a compressor and a refrigeration cycle device having the compressor that can suppress the occurrence of refrigerant leakage and seizure into a chamber.

A compressor according to the present disclosure includes a closed container forming an outer shell, an electric motor section having a stator and a rotor, a rotating shaft connected to the rotor and transmitting a driving force of the electric motor section, and the rotating shaft and a compression mechanism that compresses the refrigerant by driving force transmitted from the rotating shaft, the rotating shaft having an eccentric shaft, and the compression mechanism that is connected to the sealed container. a cylinder that is fixed and has a cylinder chamber into which refrigerant is sucked and compressed; a rolling piston that is fitted to the eccentric shaft portion and accommodated in the cylinder chamber and rotates together with the eccentric shaft portion to compress the refrigerant; a vane provided in a vane groove formed in a radial direction of the cylinder and following the rolling piston to divide the cylinder chamber into a refrigerant suction chamber and a compression chamber, the vane groove being formed in the cylinder. The vane stop portion is formed at the end of the outer peripheral surface of the cylinder without penetrating to the outer peripheral surface of the cylinder on one end surface side of the two opposing end surfaces of the cylinder, and on the other end surface side of the cylinder , the vane is formed to penetrate the outer peripheral surface of the cylinder, and the vane is located closer to the other end surface of the cylinder than the length along the radial direction of the portion located on the one end surface side of the cylinder. The length along the radial direction of the portion is configured to be longer.

The refrigeration cycle device according to the present disclosure includes at least the compressor, an outdoor heat exchanger that exchanges heat between the refrigerant flowing inside and the outdoor air, and heat between the refrigerant flowing inside and the indoor air. A refrigerating circuit in which an indoor heat exchanger for exchange and an expansion mechanism for expanding refrigerant flowing into the outdoor heat exchanger or the indoor heat exchanger are connected via refrigerant pipes. .

According to the present disclosure, the vane has a length in the radial direction of the portion located on the other end surface side of the cylinder penetrating the outer peripheral surface rather than the length along the radial direction of the portion located on the one end surface side of the cylinder in which the stop portion is formed. length along is longer. Therefore, the amount of protrusion of the vane into the cylinder chamber relative to the total length of the vane can be reduced, and the side area of the vane can be increased. Refrigerant leakage from the chamber to the low-pressure chamber and occurrence of seizure can be suppressed.

1 is a longitudinal sectional view schematically showing a compressor according to Embodiment 1; FIG. FIG. 2 is a cross-sectional view schematically showing one end face side of the cylinder at the top dead center of the compression mechanism portion of the compressor according to Embodiment 1; 4 is a cross-sectional view schematically showing the other end face side of the cylinder at the top dead center of the compression mechanism portion of the compressor according to Embodiment 1. FIG. FIG. 2 is a cross-sectional view schematically showing one end face side of the cylinder at the bottom dead center of the compression mechanism portion of the compressor according to Embodiment 1; 4 is a cross-sectional view schematically showing the other end face side of the cylinder at the bottom dead center, in the compression mechanism portion of the compressor according to Embodiment 1. FIG. FIG. 4 is a side view schematically showing a portion of the cylinder of the compressor according to Embodiment 1, in which vane grooves and vane spring housing holes are formed. FIG. 2 is a vertical cross-sectional view schematically showing a portion of the cylinder of the compressor according to Embodiment 1, in which vane grooves and vane spring housing holes are formed. FIG. 2 is a longitudinal cross-sectional view schematically showing a portion of the cylinder of the compressor according to Embodiment 1, in which a suction port is formed; 2 is a top view schematically showing vanes of the compressor according to Embodiment 1. FIG. FIG. 10 is a longitudinal sectional view of the vane shown in FIG. 9; FIG. 4 is a vertical cross-sectional view of a portion of the compression mechanism of the compressor according to Embodiment 1, schematically showing a state in which the vanes are arranged at the top dead center phase; FIG. 4 is a vertical cross-sectional view of a part of the compression mechanism of the compressor according to Embodiment 1, schematically showing a state in which the vanes are arranged at the phase of the bottom dead center; FIG. 10 is a side view schematically showing a portion in which vane grooves and vane spring housing holes are formed in Modification 1 of the cylinder of the compressor according to Embodiment 1; FIG. 10 is a side view schematically showing a portion in which vane grooves and vane spring housing holes are formed in Modification 2 of the cylinder of the compressor according to Embodiment 1; FIG. 7 is a vertical cross-sectional view schematically showing a portion in which a vane groove and a vane spring housing hole are formed in Modification 2 of the cylinder of the compressor according to Embodiment 1; FIG. 7 is an explanatory diagram schematically showing Modification 1 of the vane in the compressor according to Embodiment 1; FIG. 17 is a longitudinal sectional view of the vane shown in FIG. 16; FIG. 7 is an explanatory diagram schematically showing Modification 2 of the vane in the compressor according to Embodiment 1; FIG. 8 is an explanatory diagram schematically showing Modification 3 of the vane in the compressor according to Embodiment 1; FIG. 7 is an explanatory diagram schematically showing Modification 4 of the vane in the compressor according to Embodiment 1; 1 is a refrigerating circuit diagram of a refrigerating cycle apparatus including a compressor according to Embodiment 1. FIG. FIG. 10 is a cross-sectional view schematically showing the other end face side of the cylinder in the compression mechanism portion of the compressor according to Embodiment 2, in which the rolling piston is at the top dead center; FIG. 10 is a cross-sectional view schematically showing the other end face side of the cylinder in the compression mechanism portion of the compressor according to Embodiment 2, in a state where the phase of the rolling piston is 90° with respect to the top dead center; FIG. 10 is a cross-sectional view schematically showing the other end face side of the cylinder, which is a modification of the compression mechanism portion of the compressor according to Embodiment 2; FIG. 10 is a side view schematically showing a portion of a cylinder of a compressor according to Embodiment 2, in which vane grooves and vane spring housing holes are formed; FIG. 10 is a vertical cross-sectional view schematically showing a cylinder of a compressor according to Embodiment 3, in which the vanes are arranged at the top dead center phase; FIG. 11 is a top view schematically showing vanes of a compressor according to Embodiment 3; FIG. 28 is a cross-sectional view taken along the line CC shown in FIG. 27;

Embodiments of the present disclosure will be described below with reference to the drawings. In each figure, the same or corresponding parts are denoted by the same reference numerals, and the description thereof will be omitted or simplified as appropriate. Further, the shape, size, arrangement, etc. of the configuration described in each drawing can be changed as appropriate.

Embodiment 1.
First, a compressor 100 according to Embodiment 1 will be described. FIG. 1 is a longitudinal sectional view schematically showing a compressor 100 according to Embodiment 1. FIG. FIG. 2 is a cross-sectional view schematically showing one end surface side A of the cylinder 40 at the top dead center, which is the compression mechanism portion 4 of the compressor 100 according to Embodiment 1. As shown in FIG. FIG. 3 is a cross-sectional view schematically showing the compression mechanism portion 4 of the compressor 100 according to Embodiment 1 and showing the other end surface side B of the cylinder 40 at the top dead center. FIG. 4 is a cross-sectional view schematically showing one end surface side A of the cylinder 40 at the bottom dead center, which is the compression mechanism portion 4 of the compressor 100 according to Embodiment 1. As shown in FIG. FIG. 5 is a cross-sectional view of the compression mechanism portion 4 of the compressor 100 according to Embodiment 1, schematically showing the other end surface side B of the cylinder 40 at the bottom dead center. FIG. 6 is a side view schematically showing a portion of cylinder 40 of compressor 100 according to Embodiment 1, in which vane groove 42 and vane spring housing hole 43 are formed. FIG. 7 is a longitudinal sectional view schematically showing a portion of cylinder 40 of compressor 100 according to Embodiment 1, in which vane groove 42 and vane spring housing hole 43 are formed. FIG. 8 is a longitudinal sectional view schematically showing a portion of cylinder 40 of compressor 100 according to Embodiment 1, in which suction port 40a is formed.

The compressor 100 according to Embodiment 1 is a fluid machine that sucks a low-temperature, low-pressure refrigerant inside, compresses the sucked-in refrigerant, and discharges a high-temperature, high-pressure refrigerant to the outside. A compressor 100 shown in FIG. 1 is a single rotary compressor having one cylinder 40 as an example. Note that the compressor 100 is not limited to a single rotary compressor, and may be a rotary compressor having a plurality of cylinders 40, such as a twin rotary compressor having two cylinders 40, or may have another structure. . Incidentally, in a compressor through which a high flow rate of refrigerant flows, it is necessary to effectively reduce the pressure loss in the refrigerant suction path, so a twin rotary compressor or the like having a high flow rate and high capacity is suitable.

The compressor 100 according to the first embodiment includes, as shown in FIG. and a compression mechanism portion 4 that compresses the refrigerant by driving force transmitted from the rotating shaft 3 . Inside the sealed container 1, an electric motor section 2, a rotating shaft 3, and a compression mechanism section 4 are accommodated. The electric motor part 2 is housed in the upper part inside the sealed container 1 . The compression mechanism part 4 is accommodated in the lower part inside the sealed container 1 . The electric motor section 2 and the compression mechanism section 4 are connected via the rotating shaft 3 .

The closed container 1 is composed of an upper container 10 and a lower container 11 . The sealed container 1 is not limited to being formed from two components, the upper container 10 and the lower container 11, and may be formed from three or more components.

As shown in FIG. 1, the sealed container 1 is connected to a suction muffler 101 via a refrigerant suction pipe 12, and gas refrigerant is taken into the interior from the suction muffler 101. The intake muffler 101 is fixed to the outer surface of the lower container 11 of the closed container 1 by welding or the like. The suction muffler 101 separates the low-temperature, low-pressure refrigerant sent from the refrigeration circuit into liquid refrigerant and gas refrigerant, and prevents the liquid refrigerant from being sucked into the compression mechanism 4 as much as possible, and stores the separated liquid refrigerant. is provided to do so. This is because if the liquid refrigerant flows into the compression mechanism portion 4 and is compressed, the compressor 100 may cause the compression mechanism portion 4 to malfunction. Intake muffler 101 also functions as a muffler that reduces or eliminates noise generated by the inflowing refrigerant.

A refrigerant discharge pipe 13 for discharging the compressed refrigerant is connected to the upper portion of the sealed container 1 . The refrigerant discharge pipe 13 is a refrigerant pipe for discharging a high-pressure gas refrigerant to the outside of the sealed container 1 . The refrigerant discharge pipe 13 is joined to the upper container 10 by, for example, brazing or resistance welding while passing through the upper container 10 constituting the closed container 1 .

The inside of the sealed container 1 is filled with high-temperature and high-pressure gas refrigerant compressed by the compression mechanism 4, and refrigerating machine oil 14 used for lubricating the compression mechanism 4 is stored at the bottom. Refrigerating machine oil 14 is mainly used to lubricate sliding portions of compression mechanism 4 . An oil pump (not shown) is provided below the rotary shaft 3 . The oil pump pumps up the refrigerating machine oil 14 stored in the bottom portion of the closed container 1 as the rotating shaft 3 rotates, and supplies the oil to each sliding portion of the compression mechanism portion 4 . The compression mechanism 4 ensures mechanical lubrication by supplying oil to each sliding portion.

As shown in FIG. 1, the electric motor unit 2 is provided rotatably facing the cylindrical stator 20 fixed to the inner wall surface of the closed container 1 by shrink fitting or the like, and the inner surface of the stator 20. and a cylindrical rotor 21 that rotates by magnetic action. A rotary shaft 3 is fitted in the center of the rotor 21 . The electric motor unit 2 uses electric power supplied from an external power source to generate a rotational driving force on the rotating shaft 3 and transmits the rotational driving force to the compression mechanism unit 4 via the rotating shaft 3 . A brushless DC motor or the like is used for the electric motor unit 2, for example.

The rotary shaft 3 includes a main shaft portion 30 fixed to the rotor 21 of the electric motor portion 2, a sub-shaft portion 31 provided on the opposite side of the main shaft portion 30 across the compression mechanism portion 4, the main shaft portion 30 and the sub-shaft portion. and an eccentric shaft portion 32 provided between the portion 31 . The rotary shaft 3 is formed in the order of a main shaft portion 30, an eccentric shaft portion 32, and a sub shaft portion 31 from above to below the sealed container 1 in the axial direction. The main shaft portion 30 is fitted into the center portion of the rotor 21 of the electric motor portion 2 and fixed by shrink fitting or press fitting. The central axis of the eccentric shaft portion 32 is eccentric with respect to the central axes of the main shaft portion 30 and the sub shaft portion 31 .

The compression mechanism section 4 compresses the low-pressure gas refrigerant sucked into the low-pressure space of the sealed container 1 from the refrigerant suction pipe 12 into a high-pressure gas refrigerant by the rotational driving force supplied from the electric motor section 2. The high-pressure gas refrigerant compressed by the compression mechanism portion 4 is discharged into the sealed container 1 from above the compression mechanism portion 4 . As shown in FIGS. 1 to 8, the compression mechanism 4 includes a cylinder 40, an upper bearing 44, a lower bearing 45, a discharge muffler 46, a rolling piston 47, a vane 48, and a vane spring 49. I have.

The outer periphery of the cylinder 40 is fixed to the sealed container 1 with bolts or the like. As shown in FIG. 1, the cylinder 40 has an upper surface as one end surface side A and a lower surface as the other end surface side B. As shown in FIG. As shown in FIGS. 2 to 5, the cylinder 40 has a hollow cylindrical shape, and the hollow interior is a cylinder chamber 41 . As shown in FIG. 1 , the cylinder chamber 41 is open at both ends in the axial direction of the rotating shaft 3 . is blocked by That is, the cylinder chamber 41 is a space surrounded by the inner peripheral surface of the cylinder 40 , the inner wall surface of the upper bearing 44 and the inner wall surface of the lower bearing 45 .

As shown in FIGS. 2 to 5 and 8, the cylinder 40 is provided with a suction port 40a through which the gas refrigerant from the refrigerant suction pipe 12 passes, penetrating the cylinder chamber 41 from the outer peripheral surface. The intake port 40 a communicates the pipeline of the refrigerant intake pipe 12 and the cylinder chamber 41 .

In addition, as shown in FIGS. 2 to 7, the cylinder 40 is formed with a vane groove 42 that communicates with the cylinder chamber 41 and extends in the radial direction r about the rotating shaft 3 . As shown in FIGS. 2 to 5, the vane groove 42 penetrates the cylinder 40 in the axial direction from one end surface side A to the other end surface side B when viewed from the direction in which the outer shape of the cylinder 40 appears circular. there is A vane 48 that divides the cylinder chamber 41 into a suction chamber 41 a and a compression chamber 41 b is slidably fitted in the vane groove 42 . The suction chamber 41a is a low-pressure space and communicates with the suction port 40a. The compression chamber 41b is a high-pressure space and communicates with a discharge port 44a (see FIG. 1) for discharging the cylinder chamber 41 to the outside.

A stop portion 42 a is formed at the end of the vane groove 42 on the outer peripheral surface side of the cylinder 40 . The stop portion 42 a is provided to stop the movement of the vane 48 toward the outer peripheral surface of the cylinder 40 and limit the movement of the vane 48 so that the vane 48 does not protrude from the outer peripheral surface of the cylinder 40 . The stop portion 42a also has a function of introducing high-pressure refrigerant as a back pressure chamber. As shown in FIGS. 2 and 4, the stop portion 42a has an arc shape that opens only to the vane groove 42 when viewed from the one end surface side A of the cylinder 40. As shown in FIG.

In addition, as shown in FIGS. 6 and 7, the cylinder 40 is formed with a vane spring housing hole 43 as a space for housing the vane spring 49 and operating the vane spring 49 . The vane spring housing hole 43 is formed so as to extend in the radial direction r of the cylinder 40 . As shown in FIG. 7 , the vane spring housing hole 43 penetrates the outer peripheral surface of the cylinder 40 and does not penetrate the inner peripheral surface of the cylinder 40 . The length of the vane spring housing hole 43 is determined according to the shape of the vane spring 49 to be operated or the shape of the cylinder 40 .

As shown in FIG. 1, the upper bearing 44 is formed in a substantially inverted T shape when viewed from the side. The upper bearing 44 is provided on one end surface of the cylinder 40 on the side where the electric motor section 2 is arranged, and closes one opening of the cylinder chamber 41 in the axial direction. The upper bearing 44 is fitted to the main shaft portion 30 of the rotating shaft 3 and supports the main shaft portion 30 rotatably. The upper bearing 44 is fixed to the cylinder 40 with a common screw 5 together with the lower bearing 45 .

The upper bearing 44 is formed with a discharge port 44 a for discharging the refrigerant compressed in the compression chamber 41 b to the outside of the cylinder chamber 41 . A discharge valve (not shown) is attached to the discharge port 44a. The discharge valve is controlled at the timing of discharging the high-temperature and high-pressure gas refrigerant from the compression chamber 41b through the discharge port 44a. Specifically, the discharge valve closes the discharge port 44a when the pressure inside the compression chamber 41b is lower than the pressure inside the closed container 1 . Further, when the pressure inside the compression chamber 41b becomes higher than the pressure inside the closed container 1, the pressure inside the compression chamber 41b pushes the discharge valve upward.

As shown in FIG. 1, the lower bearing 45 is formed in a substantially T shape when viewed from the side. The lower bearing 45 is provided on the other end face of the cylinder 40 opposite to the side on which the electric motor section 2 is arranged, and closes the other axial opening of the cylinder chamber 41 . Further, the lower bearing 45 is fitted to the sub-shaft portion 31 of the rotating shaft 3 and rotatably supports the sub-shaft portion 31 .

The discharge muffler 46 is attached so as to cover the outer side of the upper bearing 44, as shown in FIG. Inside the compression chamber 41b, the actions of sucking the refrigerant, compressing the refrigerant, and discharging the refrigerant are repeated. The compressed gas refrigerant is intermittently discharged from the discharge port 44a. As a result, noise such as pulsating noise may be generated from the cylinder 40 . The discharge muffler 46 is provided to suppress noise such as pulsating noise generated from the cylinder 40 .

Further, the discharge muffler 46 is provided with a discharge hole (not shown) that communicates the space formed by the discharge muffler 46 and the upper bearing 44 with the inside of the sealed container 1 . The gas refrigerant discharged from the cylinder 40 through the discharge port 44a is once discharged into the space formed by the discharge muffler 46 and the upper bearing 44, and then discharged into the sealed container 1 through the discharge hole.

As shown in FIGS. 2 to 5, the rolling piston 47 is formed in a hollow cylindrical shape, and the eccentric shaft portion 32 of the rotating shaft 3 is slidably fitted in the hollow interior. The rolling piston 47 is housed in the cylinder chamber 41 together with the eccentric shaft portion 32 . The rolling piston 47 rotates along the inner peripheral surface of the cylinder chamber 41 and compresses the refrigerant when the rotating shaft 3 is rotated by driving the electric motor portion 2 .

As shown in FIGS. 2 to 5, the vanes 48 move inside the vane grooves 42 following the rotation of the rolling piston 47 while the tips are kept in contact with the outer peripheral surface of the rolling piston 47 during the refrigerant compression process. slide back and forth. The cylinder chamber 41 is partitioned into a suction chamber 41 a and a compression chamber 41 b by contacting the outer peripheral surface of the rolling piston 47 with the tip of the vane 48 . The vanes 48 are made of, for example, a non-magnetic material.

The vane spring 49 contacts the rear side of the vane 48 and presses the vane 48 so that the tip of the vane 48 contacts the outer peripheral surface of the rolling piston 47 . The vane spring 49 is housed in the vane spring housing hole 43 of the cylinder 40 and arranged in series with the vane 48 . As shown in FIG. 7, the vane spring 49 is fixed to the cylinder 40 by the end turn 49a press-fitted inside the vane spring housing hole 43 coming into contact with the inner wall surface of the vane spring housing hole 43. . Note that the method for fixing the vane spring 49 to the cylinder 40 is not limited to this method.

In the compression mechanism 4 configured as described above, the high-pressure gas refrigerant inside the sealed container 1 flows into the stop portion 42a, and the pressure difference between the pressure of the gas refrigerant in the stop portion 42a and the pressure of the gas refrigerant in the cylinder chamber 41 causes , create a force that moves the vane 48 in the radial direction r toward the center of the cylinder chamber 41 . In the compression mechanism 4, the pressure difference between the pressure of the gas refrigerant at the stop portion 42a and the pressure of the gas refrigerant inside the cylinder chamber 41 is sufficient to press the vane 48 against the outer peripheral surface of the rolling piston 47. It may not be pressure. Even in such a case, the vane 48 can be pressed toward the rolling piston 47 by the force of the vane spring 49 in the compression mechanism 4, so that the tip of the vane 48 is always in contact with the outer peripheral surface of the rolling piston 47. can be made

Here, the operation of the compressor 100 will be described. In the compressor 100 , the rolling piston 47 rotates together with the eccentric shaft portion 32 inside the cylinder chamber 41 when the rotary shaft 3 is rotated by driving the electric motor portion 2 . In the cylinder chamber 41, a suction chamber 41a partitioned by the vanes 48 increases in volume as the rotating shaft 3 rotates. Also, in the cylinder chamber 41, the volume of the compression chamber 41b partitioned by the vane 48 is reduced.

In the compressor 100, the suction chamber 41a communicates with the suction port 40a, and low-pressure gas refrigerant is sucked into the cylinder chamber 41. Next, the communication between the compression chamber 41b and the suction port 40a is closed by the rolling piston 47, and the gas refrigerant inside the compression chamber 41b is compressed as the volume of the compression chamber 41b decreases. Finally, the compression chamber 41b communicates with the discharge port 44a of the upper bearing 44, and after the gas refrigerant inside the compression chamber 41b reaches a predetermined pressure, the discharge valve provided at the discharge port 44a is opened and compressed. The gas refrigerant that has become high pressure and high temperature is discharged to the outside of the cylinder chamber 41 .

The high-pressure and high-temperature gas refrigerant discharged to the outside of the cylinder chamber 41 is discharged into the sealed container 1 via the discharge muffler 46 . Then, the discharged gas refrigerant passes through the inside of the electric motor part 2, rises inside the closed container 1, and is discharged to the outside of the closed container 1 from the refrigerant discharge pipe 13 provided in the upper part of the closed container 1. be done. The refrigerant discharged to the outside of the sealed container 1 circulates through the refrigeration circuit and returns to the suction muffler 101 again.

By the way, in recent years, low GWP (Global Warming Potential) refrigerants such as R32, R1234yf, or R290 have been used as refrigerants for refrigeration cycle devices equipped with compressors as one of the measures against global warming. However, low GWP refrigerants have a smaller refrigerating capacity per volume than conventionally used refrigerants such as R410A. Therefore, in the refrigerating cycle device, it is necessary to increase the flow rate of the refrigerant flowing inside in order to achieve the desired refrigerating capacity. In order to increase the flow rate of the refrigerant, it is effective to increase the stroke volume of the compression chamber 41b. The stroke volume is the amount of refrigerant discharged per rotation of the compression mechanism 4 . In order to increase this stroke volume, it is desirable to increase the inner diameter of the cylinder chamber 41 .

However, if the inner diameter of the cylinder chamber 41 is increased, the amount of protrusion of the vane 48 that protrudes into the cylinder chamber 41 increases. If the vane 48 protrudes into the cylinder chamber 41 by a large amount relative to the overall length, the operation becomes unstable, and the ability to follow the rolling piston 47 deteriorates. As a result, in the compressor 100, refrigerant leakage may occur from the compression chamber 41b (high pressure) in the cylinder chamber 41 to the suction chamber 41a (low pressure), and the compression efficiency may decrease. In addition, since the side area of the vane 48 that supports the load of the refrigerant differential pressure acting in the direction from the compression chamber 41b to the suction chamber 41a becomes smaller, severe sliding conditions occur, causing seizure and causing the compressor 100 to malfunction. Become.

Therefore, in the compressor 100 according to the first embodiment, even if the inner diameter of the cylinder chamber 41 of the cylinder 40 is increased to increase the amount of protrusion of the vane 48 that projects into the cylinder chamber 41, the pressure from the high pressure chamber to the low pressure chamber is increased. It has a configuration that can suppress the occurrence of refrigerant leakage and seizure.

Specifically, as shown in FIGS. 2 to 7, the vane groove 42 has an opening 42b formed at one end positioned on the inner peripheral side of the cylinder 40. As shown in FIGS. 2 and 3, the vane groove 42 does not penetrate to the outer peripheral surface of the cylinder 40 on the one end surface side A of the cylinder 40, which is the upper surface of the cylinder 40, and is formed on the outer peripheral surface side of the cylinder 40. A stop portion 42a for the vane 48 is formed at the end. On the other hand, as shown in FIGS. 4 and 5, the vane groove 42 is formed through the outer peripheral surface of the cylinder 40 on the other end surface side B of the cylinder 40 which is the lower surface of the cylinder 40 . In other words, the vane groove 42 functions as a stop portion 42a only on the one end surface side A of the cylinder 40 . As shown in FIG. 6, the vane spring storage hole 43 has a perfect circular cross-sectional shape perpendicular to the direction in which the vane spring storage hole 43 extends. It becomes a shape that communicates. In the illustrated example, the one end surface side A is the upper surface of the cylinder 40 and the other end surface side B is the lower surface of the cylinder 40, but the one end surface side A is the lower surface of the cylinder 40 and the other end surface side B is the upper surface of the cylinder 40. good too.

FIG. 9 is a top view schematically showing the vane 48 of the compressor 100 according to Embodiment 1. FIG. FIG. 10 is a longitudinal sectional view of vane 48 shown in FIG. FIG. 11 is a vertical cross-sectional view of a portion of the compression mechanism portion 4 of the compressor 100 according to Embodiment 1, schematically showing a state in which the vane 48 is arranged at the top dead center phase. FIG. 12 is a vertical cross-sectional view of a portion of the compression mechanism portion 4 of the compressor 100 according to Embodiment 1, schematically showing a state in which the vane 48 is arranged at the phase of the bottom dead center.

As shown in FIGS. 9 to 12, the vane 48 penetrates the outer peripheral surface of the portion 481 located on the one end surface side A of the cylinder 40 in which the stop portion 42a is formed, along the radial direction r. The length Lb along the radial direction r of the portion 482 positioned on the other end surface side B of the cylinder 40 is longer. That is, the vane 48 has a non-rectangular parallelepiped shape. The length of vanes 48 is defined by the construction of cylinder 40 . The vane 48 that follows the rolling piston 47 does not protrude from the inner peripheral surface of the cylinder chamber 41 when the rolling piston 47 is positioned at the top dead center phase, as shown in FIGS. It is completely housed in the vane groove 42. The top dead center phase is when the rolling piston 47 is positioned in the vane groove 42 phase, as shown in FIGS. In the top dead center phase, as long as the vane 48 follows the rolling piston 47, the rear side of the vane 48 does not contact the stop 42a at the portion 481 located on the one end surface side A of the cylinder 40, and the cylinder A portion 482 located on the other end surface side B of the cylinder 40 does not protrude from the outer peripheral surface of the cylinder 40 .

In addition, the vane 48 is sized so as not to protrude outside from the outer peripheral surface of the cylinder 40 when it is separated from the rolling piston 47 and pressed against the stop portion 42a. When the liquid refrigerant is sucked into the cylinder chamber 41, the vane 48 temporarily follows the rolling piston 47 in order to prevent damage or failure of the components of the compression mechanism 4 due to overload due to liquid compression. is canceled. At this time, the rear surface side of the vane 48 on the one end surface side A of the cylinder 40 is pressed against the stop portion 42a by the pressure from the high-pressure liquid refrigerant. At this time, as described above, the rear surface side of the vane 48 in the portion 482 positioned on the other end surface side B of the cylinder 40 does not protrude from the outer peripheral surface of the cylinder 40 to the outside. By ensuring that the vane 48 does not protrude from the outer peripheral surface of the cylinder 40 by the stop portion 42a, the vane 48 can be prevented from coming into contact with the closed container 1.例文帳に追加As a result, the compressor 100 can avoid the inside of the sealed container 1 from being scraped or deformed and ruptured, thereby ensuring safety.

4, 5 and 12, when the rolling piston 47 is positioned at the bottom dead center phase, the vane 48 following the rolling piston 47 protrudes from the inner peripheral surface of the cylinder chamber 41. . The phase at the bottom dead center is when the rolling piston 47 revolves 180° from the top dead center and is positioned on the opposite side of the vane groove 42 . At this time, it is geometrically defined that the amount of protrusion of the vane 48 from the inner peripheral surface of the cylinder chamber 41 is twice the amount of eccentricity e of the eccentric shaft portion 32 that determines the orbit of the rolling piston 47 . When the inner diameter of the cylinder 40 is R and the outer diameter of the rolling piston 47 is r, the eccentricity e is
e=R/2−r/2
defined in relation to Here, in the compressor 100 according to Embodiment 1, if the total length of the vane 48 at the portion 482 located on the other end surface side B of the cylinder 40 is Lb,
2e/Lb<0.5
have a relationship That is, the vane 48 is defined such that the ratio of the amount of protrusion into the cylinder chamber 41 (protrusion ratio) to the total length is less than 50%. With this provision, the sliding reciprocating motion of the vane 48 can be kept stable. Therefore, the compressor 100 can ensure a long overall length of the vanes 48 and can increase the protrusion amount of the vanes 48, so that high flow rate, high capacity and high reliability can be obtained. Regarding the length La of the vane 48 on the one end surface side A of the cylinder 40,
2e/La≧0.5
or
2e/La<0.5
may be

FIG. 13 is a side view schematically showing a first modification of the cylinder 40 of the compressor 100 according to the first embodiment, in which the vane grooves 42 and the vane spring housing holes 43 are formed. As shown in FIG. 13 , the vane spring housing hole 43 may be formed by offsetting the central axis P from the center O of the cylinder 40 in the thickness direction toward the one end surface side A of the cylinder 40 . The direction of this offset is the direction in which the length of the stop portion 42a is shortened. The length of the vane 48 along the radial direction r of the cylinder 40 is longer at the portion 482 located at the other end surface side B of the cylinder 40 than at the portion 481 located at the one end surface side A of the cylinder 40 . Therefore, the side area of the vane 48 can be increased by shortening the length of the stop portion 42a formed on the one end surface side A of the cylinder 40 . By increasing the side area of the vanes 48, the compressor 100 can sufficiently support the differential pressure between the high-pressure refrigerant and the low-pressure refrigerant, thereby further improving reliability.

FIG. 14 is a side view schematically showing a second modified example of the cylinder 40 of the compressor 100 according to the first embodiment, in which the vane grooves 42 and the vane spring housing holes 43 are formed. FIG. 15 is a longitudinal sectional view schematically showing a second modification of the cylinder 40 of the compressor 100 according to the first embodiment, in which the vane grooves 42 and the vane spring housing holes 43 are formed. As shown in FIGS. 14 and 15, when the stop portion 42a is projected onto the other end surface side B of the cylinder 40 as viewed from the one end surface side A of the cylinder 40, the outer peripheral surface of the cylinder 40 is projected from a point 420a where the stop portion 42a is projected. A groove width L1 of the vane groove 42 in the distance X is formed larger than a groove width L2 of the vane groove 42 in the distance Y from the projected portion 420a of the stop portion 42a to the inner peripheral surface of the cylinder 40 . Thereby, the processing of the vane grooves 42 can be easily performed. It should be noted that the term "from the point 420a where the stop portion 42a is projected" may be anywhere within the range of the projected point 420a.

The vane groove 42 must be formed so that the flatness is less than 10 [μm], and high processing accuracy is required. Therefore, it is difficult to machine the vane grooves 42 with the same flatness from the inner peripheral surface to the outer peripheral surface of the cylinder 40 . On the other hand, the vane groove 42 has a plane X between a point 420a where the stop portion 42a is projected and the outer peripheral surface of the cylinder 40, and a plane Y between a point 420a where the stop portion 42a is projected and the inner peripheral surface of the cylinder 40. and are formed as separate planes, processing becomes easier. Here, the sliding conditions of the vane 48 and the vane groove 42 are the severest when the rolling piston 47 is in the phase of the bottom dead center. However, the portion X from the point 420a where the stop portion 42a is projected to the outer peripheral surface of the cylinder 40 has a low contribution rate to the sliding conditions. Therefore, in the compressor 100, there is a plane X between a point 420a where the stop 42a is projected and the outer peripheral surface of the cylinder 40, and a plane Y between the point 420a where the stop 42a is projected and the inner peripheral surface of the cylinder 40. Even if it is machined as a separate plane from the sliding surface, it has little effect on the sliding conditions.

FIG. 16 is an explanatory diagram schematically showing Modification 1 of the vane 48 in the compressor 100 according to Embodiment 1. FIG. FIG. 17 is a longitudinal sectional view of vane 48 shown in FIG. As shown in FIGS. 16 and 17, the vane 48 may have an introduction groove 48a formed in the end surface of the portion 482 located on the other end surface side B of the cylinder 40 for introducing the high-pressure gas refrigerant. The introduction groove 48 a is formed along the radial direction r of the cylinder 40 . The vane 48 has an asymmetrical structure between a portion 481 located on one end surface side A of the cylinder 40 and a portion 482 located on the other end surface side B of the cylinder 40. During operation, the vane 48 performs an unbalanced reciprocating motion, resulting in local sliding. It may come into direct contact with the surface, causing seizure and galling. The vane 48 is provided with the introduction groove 48a for the high-pressure gas refrigerant, so that a load can be applied from above and below the cylinder 40, and the balance of the entire reciprocating motion can be improved. The introduction groove 48 a communicates with the back surface side of the vane 48 , but does not communicate with the tip end side that contacts the rolling piston 47 . This is because if the introduction groove 48a communicates with the leading end side, the high-pressure gas refrigerant outside the compression mechanism 4 communicates with the low-pressure refrigerant inside the compression chamber 41b, and the efficiency of the compressor 100 decreases. be. The vane 48 may have a configuration in which the introduction groove 48a is formed in the end surface of the portion 481 located on the one end surface side A of the cylinder 40, or the portion 481 located on the one end surface side A of the cylinder 40 and the other end surface side. A configuration in which the introduction grooves 48a are formed in both end surfaces of the portion 482 located at B may be employed.

FIG. 18 is an explanatory view schematically showing Modification 2 of vane 48 in compressor 100 according to Embodiment 1. FIG. FIG. 19 is an explanatory diagram schematically showing Modification 3 of vane 48 in the compressor according to Embodiment 1. As shown in FIG. In the vane 48 shown in FIG. 18, the entire rear surface of the portion 481 located on the one end surface side A of the cylinder 40 where the stop portion 42a is formed is formed into an R shape 48b. In the compressor 100 according to Embodiment 1, only one end surface side A of the cylinder 40 is provided with the stop portion 42a. As such, the stop 42a has a shorter length to receive the vane 48 than in conventional compressors. Therefore, the stress generated when the back surface of the vane 48 collides with the stop portion 42a increases, and the parts are likely to be scraped or worn. On the other hand, by forming the back surface of the vane 48 into the rounded shape 48b, the generation of local stress due to corner contact can be suppressed, and the situation in which parts are chipped or worn can be suppressed. In addition, as shown in FIG. 19, the vane 48 may have a rounded shape 48b only at the corners of the rear surface of the portion 481 located on the one end surface side of the cylinder 40 where the stop portion 42a is formed.

FIG. 20 is an explanatory diagram schematically showing Modification 4 of vanes 48 in compressor 100 according to Embodiment 1. FIG. The vane 48 shown in FIG. 20 has a central portion 483 extending along the radial direction r of the cylinder 40 between a portion 481 located on one end surface side A of the cylinder 40 and a portion 482 located on the other end surface side B. is provided. The central portion 483 is configured to be inserted inside the vane spring 49, and when the rolling piston 47 is positioned at the top dead center phase, the back surface thereof is located closer to the outer peripheral surface side of the cylinder 40 than the end turn 49a of the vane spring 49. ing. Since the vane 48 shown in FIG. 20 has a central portion 483, the side area can be increased, so that the load of the refrigerant differential pressure applied in the direction from the compression chamber 41b (high pressure) to the suction chamber 41a (low pressure) can be reduced. I can support it enough.

Here, the dimensions of the cylinder 40 in the compressor 100 according to Embodiment 1 will be explained. In addition, the dimensions of the cylinder 40 shown below are an example, and are not limited to the dimensions. The thickness of the cylinder 40 is, for example, 30 [mm]. The outer diameter of the cylinder 40 is assumed to be 130 [mm]. The inner diameter of the cylinder 40 is assumed to be 60 [mm]. The difference in radius between the inner diameter and the outer diameter of the cylinder 40 is 35 [mm]. The diameter of the vane spring housing hole 43 is 14 [mm]. The width of the vane groove 42 and the vane 48 is 4 [mm]. A clearance formed by the vane groove 42 and the vane 48 is 30 [μm].

The diameter of the stop portion 42a is 9 [mm]. When the center of the vane spring housing hole 43 is aligned with the center of the cylinder 40, the length of the stop portion 42a is (thickness 30 [mm] of the cylinder 40-spring diameter 14 [mm])/2=8 [ mm]. Here, as shown in FIG. 13, when the center of the vane spring housing hole 43 is offset to the one end surface side A and the offset amount is 2 mm, the length of the stop portion 42a is reduced by that amount to 6 mm. mm]. Further, as shown in FIGS. 16 and 17, when the introduction groove 48a is formed in the vane 48, the width of the vane 48 is 4 [mm], the groove width of the introduction groove 48a is 2 [mm], and the depth is It is 1 [mm].

As for the total length of the vane 48, the length La of the portion 481 located on the one end surface side A of the cylinder 40 is 30 mm, and the length Lb of the portion 482 located on the other end surface side B of the cylinder 40 is 34.4 mm. [mm]. At the top dead center when the vane 48 follows the rolling piston 47, the distance to the interference between the stop portion 42a and the back surface of the vane 48 is 0.5 [mm]. Therefore, as long as the vane 48 keeps following the rolling piston 47, the vane 48 does not come into contact with the stop portion 42a. Further, even when the vane 48 is released from following the rolling piston 47 and the rear surface of the vane 48 contacts the stop portion 42a, the vane 48 is still positioned so that the rear surface of the portion 482 located on the other end surface side B of the cylinder 40 Do not protrude outside from the outer peripheral surface of

As described above, the compressor 100 according to the first embodiment includes the closed container 1 forming the outer shell, the electric motor section 2 having the stator 20 and the rotor 21, and the electric motor section 2 connected to the rotor 21. and a compression mechanism 4 connected to the rotating shaft 3 for compressing the refrigerant by the driving force transmitted from the rotating shaft 3 . The rotating shaft 3 has an eccentric shaft portion 32 . The compression mechanism portion 4 is fixed to the sealed container 1 and is fitted with a cylinder 40 having a cylinder chamber 41 into which refrigerant is sucked and compressed, and an eccentric shaft portion 32 which is accommodated in the cylinder chamber 41 . A rolling piston 47 that rotates together to compress the refrigerant, and a vane groove 42 formed in the radial direction r of the cylinder 40 follow the rolling piston 47 to form the cylinder chamber 41 into a refrigerant suction chamber 41a and a refrigerant compression chamber 41b. and a vane 48 that separates the The vane groove 42 does not penetrate to the outer peripheral surface of the cylinder 40 on one end surface side A of the two opposing end surfaces of the cylinder 40, and the stop portion 42a of the vane 48 is formed at the end portion on the outer peripheral surface side of the cylinder 40. , and is formed so as to penetrate the outer peripheral surface of the cylinder 40 on the other end surface side B of the cylinder 40 . The vane 48 has a length Lb along the radial direction r of the portion 482 located on the other end surface side B of the cylinder 40 that is longer than the length La along the radial direction r of the portion 481 located on the one end surface side A of the cylinder 40 . is considered to be longer.

Therefore, according to the compressor 100 according to Embodiment 1, the amount of protrusion of the vanes 48 into the cylinder chamber 41 relative to the total length of the vanes 48 can be reduced, and the side area of the vanes 48 can be increased. Therefore, even if the inner diameter of the cylinder chamber 41 of the cylinder 40 is increased to increase the amount of protrusion of the vane 48, it is possible to suppress refrigerant leakage and seizure from the high-pressure compression chamber 41b to the low-pressure suction chamber 41a. .

Next, based on FIG. 21, a refrigeration cycle device 200 including the compressor 100 according to Embodiment 1 will be described. FIG. 21 is a refrigeration circuit diagram of refrigeration cycle apparatus 200 including compressor 100 according to Embodiment 1. As shown in FIG.

As shown in FIG. 21, the refrigeration cycle apparatus 200 according to Embodiment 1 includes a compressor 100, a flow path switching device 102, an outdoor heat exchanger 103, an expansion mechanism 104, an indoor heat exchanger 105, and an intake The muffler 101 has a refrigerating circuit 107 which is sequentially connected by a refrigerant pipe 106 and in which the refrigerant circulates.

　R407C refrigerant, R410A refrigerant, R32 refrigerant, or the like is used as the refrigerant flowing through the refrigeration circuit 107 . The efficiency of the compressor 100 can be further improved by using a low GWP refrigerant such as R1234yf refrigerant or R290 refrigerant.

The channel switching device 102 is, for example, a four-way valve and has a function of switching the coolant channel. During cooling operation, the flow switching device 102 connects the refrigerant discharge side of the compressor 100 and the gas side of the outdoor heat exchanger 103, and also connects the refrigerant suction side of the compressor 100 and the indoor heat exchanger 105. Switch the refrigerant flow path so as to connect the gas side. On the other hand, during heating operation, the flow switching device 102 connects the refrigerant discharge side of the compressor 100 and the gas side of the indoor heat exchanger 105, and connects the refrigerant suction side of the compressor 100 to the outdoor heat exchanger. The refrigerant flow path is switched so as to connect the gas side of 103 . Note that the flow path switching device 102 may be configured by combining two-way valves or three-way valves.

The outdoor heat exchanger 103 functions as a condenser during cooling operation, and performs heat exchange between the refrigerant discharged from the compressor 100 and flowing inside and the outdoor air. Further, the outdoor heat exchanger 103 functions as an evaporator during heating operation, and performs heat exchange between the refrigerant flowing out from the expansion mechanism 104 and flowing inside and the outdoor air. The outdoor heat exchanger 103 draws in outdoor air using an air blower (not shown) and discharges the air heat-exchanged with the refrigerant to the outside.

The expansion mechanism 104 decompresses and expands the refrigerant that has flowed out of the condenser, and is composed of, for example, an electronic expansion valve that can adjust the opening of a throttle. The expansion mechanism 104 controls the pressure of the refrigerant flowing into the outdoor heat exchanger 103 or the indoor heat exchanger 105 by adjusting the degree of opening.

The indoor heat exchanger 105 functions as an evaporator during cooling operation, and performs heat exchange between the refrigerant flowing out from the expansion mechanism 104 and flowing inside and the indoor air. In addition, the indoor heat exchanger 105 functions as a condenser during heating operation, and performs heat exchange between the refrigerant discharged from the compressor 100 and flowing inside and the indoor air. The indoor-side heat exchanger 105 draws in indoor air using an air blower (not shown), and supplies the air, which has been heat-exchanged with the refrigerant, indoors.

Next, the operation of the refrigeration cycle device 200 during heating operation will be described. In the heating operation of the air conditioner, the pipes connected to the flow path switching device 102 are connected so as to form a circuit on the solid line side in FIG. The high-temperature and high-pressure gas refrigerant discharged from the compressor 100 passes through the flow path switching device 102 and flows to the indoor heat exchanger 105, exchanges heat with air, and is condensed and liquefied. The condensed and liquefied refrigerant is decompressed by the expansion mechanism 104 to become a low-temperature, low-pressure gas-liquid two-phase refrigerant, flows to the outdoor heat exchanger 103, exchanges heat with air, and is gasified. The gasified refrigerant passes through the flow switching device 102 and is sucked into the compressor 100 via the suction muffler 101 .

Next, the operation of the refrigeration cycle device 200 during cooling operation will be described. In the cooling operation of the air conditioner, the pipes connected to the flow path switching device 102 are connected to each other so as to form a circuit on the dashed line side in FIG. The high-temperature and high-pressure gas refrigerant discharged from the compressor 100 passes through the flow path switching device 102 and flows to the outdoor heat exchanger 103, exchanges heat with the air, and condenses and liquefies. The condensed and liquefied refrigerant is decompressed by the expansion mechanism 104 to become a low-temperature, low-pressure gas-liquid two-phase refrigerant, flows to the indoor heat exchanger 105, exchanges heat with air, and is gasified. The gasified refrigerant passes through the flow switching device 102 and is sucked into the compressor 100 via the suction muffler 101 .

A refrigeration cycle device 200 includes the compressor 100 according to the first embodiment. Therefore, refrigeration cycle device 200 can obtain the same effects as compressor 100 according to the first embodiment.

Embodiment 2.
Next, the compressor 100 according to the second embodiment will be described with reference to FIGS. 22 to 25. FIG. FIG. 22 is a compression mechanism portion 4 of the compressor 100 according to Embodiment 2, and is a cross-sectional view schematically showing the other end surface side B of the cylinder 40 in a state where the rolling piston 47 is at the top dead center. . FIG. 23 schematically shows the compression mechanism portion 4 of the compressor 100 according to Embodiment 2, and the other end surface side B of the cylinder 40 in a state where the phase of the rolling piston 47 is 90° with respect to the top dead center. 1 is a cross sectional view shown; FIG. FIG. 24 is a cross-sectional view schematically showing the other end surface side B of the cylinder 40, which is a modification of the compression mechanism portion 4 of the compressor 100 according to Embodiment 2. As shown in FIG. FIG. 25 is a side view schematically showing a portion of cylinder 40 of compressor 100 according to Embodiment 2, in which vane groove 42 and vane spring housing hole 43 are formed. The same components as those of the compressor 100 described in Embodiment 1 are denoted by the same reference numerals, and the description thereof will be omitted as appropriate.

As shown in FIGS. 22 and 23, the sealed container 1 is formed with through holes 10a at positions corresponding to the vane grooves 42, in which the vanes 48 can slide. The through hole 10 a is closed from the outer peripheral surface side of the closed container 1 by a closing component 15 which is a separate component from the closed container 1 . Other configurations are the same as those of the compressor 100 described in the first embodiment.

As shown in FIG. 22, when the rolling piston 47 is positioned at the top dead center phase, the vane 48 has a portion located on the other end surface side B of the cylinder 40 extending from the outer peripheral surface of the cylinder 40 to the through hole 10a. protrude. By allowing the vanes 48 to protrude from the outer peripheral surface of the cylinder 40, the length of the vanes 48 in the radial direction r of the cylinder 40 can be increased. In the compressor 100, by increasing the total length of the vanes 48, the sliding conditions of the vanes 48 and the vane grooves 42 can be relaxed, so pressure loss can be reduced, compressor efficiency can be improved, and reliability can be further improved. improves.

Note that the compressor 100 according to Embodiment 2 is not limited to the configuration in which the closed container 1 is formed with the through hole 10a. As shown in FIG. 24, pressing or the like may be performed to form recesses 10b in which the vanes 48 can rub on the inner wall surface of the sealed container 1, thereby forming a configuration corresponding to the through holes 10a. The vane 48 protrudes from the outer peripheral surface of the cylinder 40 into the recess 10b when the rolling piston 47 is positioned at the top dead center phase.

Also, in the compressor 100 according to the second embodiment, it is necessary to increase the force of the vane springs 49 that press the vanes 48 by increasing the total length of the vanes 48 . If the pressing load of the vane spring 49 is insufficient, the vane 48 and the rolling piston 47 are separated near the bottom dead center, the partition between the suction chamber 41a and the compression chamber 41b is released, and the efficiency of the compressor 100 may decrease. be. Therefore, as shown in FIG. 25, the cylinder 40 is formed with a groove portion 43 a extending from the vane spring housing hole 43 toward the cylinder chamber 41 . The vane spring 49 is slidably fitted inside the groove portion 43a. The movement of the vane spring 49 is allowed by the groove 43a, so that the pressing force of the vane spring 49 at the bottom dead center can be secured. In addition, the configuration in which the groove portion 43a is formed in the vane spring housing hole 43 is not limited to the configuration of the second embodiment, and can also be applied to the other first or third embodiments.

In the case of a single rotary compressor having one cylinder 40, the vane 48 does not protrude from the outer peripheral surface of the cylinder 40 when the revolution phase of the rolling piston 47 is 180° with respect to the top dead center. dimensions are desirable. This is because, although the total length of the vane 48 is limited, it is difficult to attach the compression mechanism 4 to the closed container 1 if the vane 48 always protrudes from the outer peripheral surface of the cylinder 40 .

On the other hand, in the case of a twin rotary compressor having two cylinders 40, as shown in FIG. , the vane 48 is desirably sized such that the rear side thereof does not protrude from the outer peripheral surface of the cylinder 40 . In the twin rotary compressor, the rolling pistons 47 provided in the respective cylinders 40 rotate with 180° different revolution phases. In other words, with the above configuration, it is possible to prevent the rear side of any of the vanes 48 of the two cylinders 40 from constantly protruding from the outer peripheral surface of the cylinder 40 to the outside.

Embodiment 3.
Next, the compressor 100 according to Embodiment 3 will be described with reference to FIGS. 26 to 28. FIG. FIG. 26 is a vertical cross-sectional view schematically showing cylinder 40 of compressor 100 according to Embodiment 3, in which vane 48 is arranged at the top dead center phase. FIG. 27 is a top view schematically showing vane 48 of compressor 100 according to the third embodiment. 28 is a cross-sectional view taken along the line CC shown in FIG. 27. FIG. The same components as those of the compressor 100 described in

Embodiments

1 and 2 are denoted by the same reference numerals, and description thereof will be omitted as appropriate.

As shown in FIG. 26 , the vane grooves 42 do not penetrate to the outer peripheral surface side of the cylinder 40 on one end surface side A of the two opposing end surfaces of the cylinder 40 , but extend to the end portion on the outer peripheral surface side of the cylinder 40 . A first stop 42c of the vane 48 is formed. Further, the vane groove 42 does not penetrate to the outer peripheral surface of the cylinder 40 on the other end surface side B of the cylinder 40, and a second stopping portion 42d of the vane 48 is formed at the end portion on the outer peripheral surface side of the cylinder 40. . That is, the vane groove 42 has

stop portions

42 c and 42 d formed on one end surface side A and the other end surface side B of the cylinder 40 . The vane spring storage hole 43 has a perfect circular cross-sectional shape perpendicular to the direction in which the vane spring storage hole 43 extends.

As shown in FIGS. 27 and 28, the vane 48 has a portion 481 located on one end surface side A of the cylinder 40 where the first stop portion 42c is formed and the other end surface side B where the second stop portion 42d is formed. A central portion 483 extending along the radial direction r of the cylinder 40 is provided between the portion 482 located at the . The central portion 483 is such that the length Lc along the radial direction r of the cylinder 40 is equal to the length La along the radial direction r of the portion 481 located on the one end surface side A of the cylinder 40 and the portion 482 located on the other end surface side B of the cylinder 40 . It is longer than the length Lb in the radial direction r. The vane 48 is formed such that the length La of the portion 481 located on the one end surface side A of the cylinder 40 and the length Lb of the portion 482 located on the other end surface side B are substantially equal. Further, as shown in FIG. 26, the central portion 483 is configured to be inserted inside the vane spring 49, and when the rolling piston 47 is arranged at the phase of the top dead center, the back surface of the vane spring 49 reaches the end turn 49a of the vane spring 49. is positioned closer to the outer peripheral surface of the cylinder 40 than the .

In the compressor 100 according to Embodiment 3, the length La of the portion 481 located on the one end surface side A of the cylinder 40 and the length Lb of the portion 482 located on the other end surface side B of the vane 48 are substantially equal to each other. Since they are formed with the same length, the vertical balance during the reciprocating motion of the vane 48 can be stabilized. The vane groove 42 is also provided with two

stop portions

42c and 42d. Therefore, even when the vane 48 comes into contact with the

stop portions

42c and 42d, the vertical balance of the vane 48 can be stabilized. In addition, since the vane 48 has the central portion 483, the side area of the vane 48 can be increased. can support

Also in the compressor 100 according to the third embodiment, for example, as shown in FIGS. Either one or both of the end faces of 482 may be formed with introduction grooves 48a for introducing high-pressure gas refrigerant.

In addition, as shown in FIG. 18, for example, the vane 48 may have an R shape 48b on the entire back surface of a portion 481 located on the one end surface side A of the cylinder 40 where the first stop portion 42c is formed. Further, the vane 48 may have an R shape 48b on the entire back surface of the portion 482 located on the other end surface side B of the cylinder 40 where the second stop portion 42d is formed. Further, as shown in FIG. 19, for example, the vane 48 may have a curved shape 48b only at the corners of the rear surface of the portion 481 located on the one end surface side A of the cylinder 40 where the first stop portion 42c is formed. Also, the vane 48 may have a rounded shape 48b only at the rear corner of the portion 481 located on the other end surface side B of the cylinder 40 where the second stop portion 42d is formed.

Although the compressor 100 and the refrigeration cycle device 200 have been described above based on the embodiment, they are not limited to the configurations of the embodiment described above. For example, the compressor 100 and the refrigeration cycle device 200 are not limited to the illustrated configurations, and may include other components. In short, the compressor 100 and the refrigerating cycle device 200 include a range of design changes and application variations that are normally made by those skilled in the art within a range that does not deviate from the technical idea thereof.

1 closed container, 2 electric motor part, 3 rotating shaft, 4 compression mechanism part, 5 screw, 10 upper container, 10a through hole, 10b recessed part, 11 lower container, 12 refrigerant intake pipe, 13 refrigerant discharge pipe, 14 refrigerator oil, 15 Closing part 20 Stator 21 Rotor 30 Main shaft 31 Sub shaft 32 Eccentric shaft 40 Cylinder 40a Suction port 41 Cylinder chamber

41a Suction chamber

41b Compression chamber 42 Vane groove 42a Stop part, 42b opening, 42c first stop, 42d second stop, 43 vane spring storage hole, 43a groove, 44 upper bearing, 44a discharge port, 45 lower bearing, 46 discharge muffler, 47 rolling piston, 48 vane, 48a introduction groove, 48b R shape, 49 vane spring, 49a end winding, 100 compressor, 101 intake muffler, 102 flow switching device, 103 outdoor heat exchanger, 104 expansion mechanism, 105 indoor heat exchanger, 106 refrigerant Piping, 107 Refrigeration circuit, 200 Refrigeration cycle device, 420a Projected portion of the end portion, 481 Portion of vane located on one end surface side of cylinder, 482 Portion of vane located on the other end surface side of cylinder, 483 Central portion, A One end face side, B other end face side, r radial direction.

Claims

a closed container forming an outer shell;
an electric motor section having a stator and a rotor;
a rotating shaft connected to the rotor and transmitting the driving force of the electric motor unit;
a compression mechanism unit that is connected to the rotating shaft and compresses a refrigerant by driving force transmitted from the rotating shaft;
The rotating shaft has an eccentric shaft portion,
The compression mechanism section is
a cylinder fixed to the sealed container and having a cylinder chamber into which a refrigerant is sucked and compressed;
a rolling piston that is fitted to the eccentric shaft portion and housed in the cylinder chamber and that rotates together with the eccentric shaft portion to compress refrigerant;
a vane provided in a vane groove formed in the radial direction of the cylinder and following the rolling piston to divide the cylinder chamber into a refrigerant suction chamber and a compression chamber;
The vane groove does not penetrate to the outer peripheral surface of the cylinder on one of the two opposing end surfaces of the cylinder, and a stop portion of the vane is formed at the end on the outer peripheral surface side of the cylinder, is formed through the outer peripheral surface of the cylinder on the other end surface side of the cylinder,
In the vane, the length along the radial direction of the portion located on the other end surface side of the cylinder is longer than the length along the radial direction of the portion located on the one end surface side of the cylinder. Compressor.
In a state in which the vane follows the rolling piston, a portion of the cylinder located on the one end surface side does not contact the stop portion and is separated from the rolling piston so that the vane is pushed against the stop portion. 2. The compressor according to claim 1, wherein a portion of said cylinder located on said other end surface side is sized so as not to protrude outside from an outer peripheral surface of said cylinder in a state of being applied.
Letting Lb be the total length of the vane in the portion located on the other end face side of the cylinder, and let e be the eccentricity of the eccentric shaft portion that determines the orbit of the rolling piston,
2×e/Lb<0.5
3. The compressor according to claim 1 or 2, wherein the relationship is:
When the stop portion is projected onto the other end surface side of the cylinder as viewed from the one end surface side of the cylinder, the groove width of the vane groove between the projected portion of the stop portion and the outer peripheral surface of the cylinder is: 4. The compressor according to any one of claims 1 to 3, wherein the vane groove is formed to have a groove width greater than a groove width of the vane groove between a portion where the stop portion is projected and an inner peripheral surface of the cylinder.
The vane according to any one of claims 1 to 4, wherein the entire back surface of the portion located on the one end surface side of the cylinder is R-shaped, or the corner of the back surface is R-shaped. compressor.
The inner wall surface of the closed container is formed with a recess in which the vane can slide,
The vane has a portion located on the other end surface side of the cylinder when the rolling piston is arranged at the phase of the top dead center, wherein the vane protrudes from the outer peripheral surface of the cylinder into the recess. 6. The compressor according to any one of 5.
7. The recess according to claim 6, wherein the recess is formed by a through hole formed at a position corresponding to the vane groove of the closed container, and a closing component closing the through hole from the outer peripheral surface side of the closed container. Compressor as described.
When the phase of the top dead center of the vane is 0° and the revolution phase of the rolling piston is 90° or 270°, the portion located on the other end surface side of the cylinder extends outward from the outer peripheral surface of the cylinder. 8. A compressor according to claim 6 or 7, having a non-protruding length.
further comprising a vane spring that presses the vane so that the tip of the vane contacts the outer peripheral surface of the rolling piston;
The compressor according to any one of claims 1 to 8, wherein said cylinder is formed with a vane spring housing hole for housing said vane spring.
The compressor according to claim 9, wherein the vane spring housing hole is formed with a central axis offset from the center of the cylinder in the thickness direction toward the one end surface of the cylinder.
The vane is provided with a central portion extending along the radial direction of the cylinder between a portion located on the one end surface side of the cylinder and a portion located on the other end surface side of the cylinder. Item 11. The compressor according to Item 9 or 10.
The central portion is configured to enter the inside of the vane spring, and when the rolling piston is positioned at the top dead center phase, the back surface is positioned closer to the outer peripheral surface of the cylinder than the end turn of the vane spring. 12. The compressor of claim 11, wherein
a closed container forming an outer shell;
an electric motor section having a stator and a rotor;
a rotating shaft connected to the rotor and transmitting the driving force of the electric motor unit;
a compression mechanism unit that is connected to the rotating shaft and compresses a refrigerant by driving force transmitted from the rotating shaft;
The rotating shaft has an eccentric shaft portion,
The compression mechanism section is
a cylinder fixed to the sealed container and having a cylinder chamber into which a refrigerant is sucked and compressed;
a rolling piston that is fitted to the eccentric shaft portion and housed in the cylinder chamber and that rotates together with the eccentric shaft portion to compress refrigerant;
a vane provided in a vane groove formed in the radial direction of the cylinder and following the rolling piston to divide the cylinder chamber into a refrigerant suction chamber and a compression chamber;
The vane groove does not penetrate to the outer peripheral surface of the cylinder on one of the opposing end surfaces of the cylinder, and the vane has a first stop portion formed at the end on the outer peripheral surface side of the cylinder, A second stop portion of the vane is formed at an end portion of the outer peripheral surface of the cylinder without penetrating to the outer peripheral surface of the cylinder on the other end surface side of the cylinder,
The vane has a central portion extending along the radial direction of the cylinder between a portion located on the one end surface side of the cylinder and a portion located on the other end surface side of the cylinder,
In the compressor, the length of the central portion along the radial direction of the cylinder is longer than the lengths of the portion located on the one end surface side and the portion located on the other end surface side of the cylinder in the radial direction.
further comprising a vane spring that presses the vane so that the tip of the vane contacts the outer peripheral surface of the rolling piston;
A vane spring housing hole for housing the vane spring is formed in the cylinder,
The central portion is configured to enter the inside of the vane spring, and when the rolling piston is positioned at the top dead center phase, the back surface is positioned closer to the outer peripheral surface of the cylinder than the end turn of the vane spring. 14. The compressor of claim 13, wherein
15. The vane according to claim 13 or 14, wherein the entire back surface of the portion located on the one end surface side and the other end surface side of the cylinder is R-shaped, or the corners of the back surface are R-shaped. compressor.
A groove portion extending the vane spring housing hole is formed in the cylinder from an end portion of the vane spring housing hole toward the cylinder chamber,
15. A compressor according to claim 9, 10, 11, 12 or 14, wherein said vane spring is slidably fitted inside said groove.
The compressor according to any one of claims 1 to 16, wherein introduction grooves for introducing high-pressure gas refrigerant staying in the sealed container are formed in the vanes along the radial direction.
At least the compressor according to any one of claims 1 to 17;
an outdoor heat exchanger that exchanges heat between the refrigerant flowing inside and the outdoor air;
an indoor heat exchanger that exchanges heat between the refrigerant flowing inside and the indoor air;
A refrigeration cycle apparatus comprising a refrigeration circuit connected via a refrigerant pipe to an expansion mechanism that expands refrigerant flowing into the outdoor heat exchanger or the indoor heat exchanger.