JP7466692B2 - Compressor and refrigeration cycle device - Google Patents

Description

The present disclosure relates to a compressor and a refrigeration cycle device having a refrigerant discharge mechanism.

Conventionally, there has been a compressor in which a valve element is placed inside the discharge port when the discharge port is closed, and the valve element is moved back and forth by a spring, thereby reducing the dead volume (see, for example, Patent Document 1).

Japanese Patent Application Laid-Open No. 8-319973

In conventional compressors, a valve disc is placed inside the discharge port and reciprocates with a spring. When this happens, the valve disc comes into contact with the wall of the discharge port, causing jamming. Jamming causes the valve disc to wear out. When the valve disc wears out, there is a problem that the efficiency of the compressor decreases and it breaks down due to poor closing of the compression chamber.

This disclosure has been made in consideration of the above-mentioned situation, and aims to provide a compressor and a refrigeration cycle device that can suppress jamming of the valve body, improve compressor efficiency, and suppress breakdowns.

The compressor according to the present disclosure comprises a sealed container, a cylinder provided within the sealed container and having a compression chamber therein in which a refrigerant is compressed, a main shaft provided within the sealed container, a bearing provided on the main shaft and having a discharge port through which the refrigerant compressed in the compression chamber is discharged, a guide lid provided on the bearing and having a guide hole therein, and a valve body provided within the guide hole, and a discharge mechanism in which the valve body moves within the guide hole to open and close the discharge port, and a communication hole is formed in the guide lid that communicates the guide hole with the inside of the sealed container from which the refrigerant discharged from the discharge port is discharged, and refrigeration oil remaining in the sealed container is supplied to the communication hole.

According to the present disclosure, the guide lid is formed with a communication hole that communicates between the guide hole and the inside of the sealed container into which the refrigerant discharged from the discharge port is discharged. Refrigeration oil is supplied to the communication hole. The valve body moves within the guide hole to open and close the discharge port. The refrigeration oil supplied to the communication hole passes through the guide hole and flows into the gap between the valve body and the side of the guide hole. Therefore, the occurrence of jamming of the valve body is suppressed in the compressor, improving the efficiency of the compressor and suppressing breakdowns.

1 is a schematic configuration diagram illustrating a configuration of a compressor according to a first embodiment. FIG. 4 is a diagram showing a state in which a valve body of the discharge mechanism of the compressor according to the first embodiment closes a discharge port. FIG. 4 is a diagram showing a state in which a valve body of a discharge mechanism of the compressor according to the first embodiment opens a discharge port. FIG. 13A to 13C are diagrams for explaining a method of supplying oil to a communication hole of a discharge mechanism of a compressor according to a second embodiment. 13A to 13C are diagrams for explaining a method of supplying oil to a communication hole of a discharge mechanism of a compressor according to embodiment 3. 13 is a diagram showing a linear oil supply groove provided in a discharge mechanism of a compressor according to embodiment 4. FIG. 13 is a diagram showing a spiral oil supply groove provided in a discharge mechanism of a compressor according to embodiment 4. FIG. FIG. 13 is a refrigerant circuit diagram illustrating a refrigerant circuit configuration of a refrigeration cycle device according to a fifth embodiment. FIG. 2 is a diagram showing the gas density of the refrigerant sucked into a compressor and the gas density of the refrigerant discharged from the compressor under rated operating conditions of the compressor in a typical refrigeration cycle defined by ASHRAE, for each refrigerant. FIG. 2 is a diagram illustrating an example of a reed valve of a compressor. 13 is a diagram for explaining a lift distance of a valve body of a compressor used in a refrigeration cycle apparatus of embodiment 6. FIG.

The compressor according to the embodiment will be described below with reference to the drawings. In the drawings, the same components are denoted by the same reference numerals, and duplicated descriptions will be provided only when necessary. The present disclosure may include any combination of the configurations described in the following embodiments that can be combined. In addition, the size relationship of each component may differ from the actual relationship in the drawings. The configurations of the components shown in the entire specification are merely examples and are not limited to the configurations described in the specification. In particular, the combination of components is not limited to the combinations in each embodiment, and components described in other embodiments may be applied to other embodiments. In addition, the high and low levels of pressure and temperature are not determined in relation to absolute values, but are determined relatively in the state and operation of the device, etc. In the following description, the longitudinal direction of the sealed container (the vertical direction in the drawing) is the axial direction, and the direction passing through the central axis of the sealed container and perpendicular to the central axis is the radial direction.

Embodiment 1.
FIG. 1 is a schematic diagram illustrating the configuration of a compressor 100 according to a first embodiment.

Compressor 100 will be described with reference to Figure 1. Compressor 100 is a component part of a refrigerant circuit of a refrigeration cycle device such as a refrigerator, a freezer, a vending machine, an air conditioner, a refrigeration system, or a water heater. Note that Figure 1 illustrates a rotary compressor as an example of compressor 100. Compressor 100 can also be applied to a hermetic compressor having a discharge valve, such as a scroll compressor or a reciprocating compressor. Also, here, the fluid compressed by compressor 100 will be described as a refrigerant used in a refrigeration cycle device or the like.

[Configuration of compressor 100]
The compressor 100 compresses and discharges the sucked refrigerant. The compressor 100 includes a sealed container 3. The sealed container 3 is composed of a lower container 1 and an upper container 2. A compression mechanism unit 10 and an electric motor unit 20 are housed in the sealed container 3. For example, FIG. 1 shows an example in which the compression mechanism unit 10 is housed in the lower side of the sealed container 3 and the electric motor unit 20 is housed in the upper side of the sealed container 3. The bottom of the sealed container 3 functions as an oil reservoir in which refrigeration oil is stored. The refrigeration oil mainly lubricates the sliding parts of the compression mechanism unit 10.

The lower container 1 of the sealed container 3 is connected to the first suction pipe 31a and the second suction pipe 31b, which are connected to the accumulator 300 (see FIG. 8). The inlets of the first suction pipe 31a and the second suction pipe 31b are inserted into the suction muffler 60. The suction port 50 of the first suction pipe 31a is formed in the cylinder 13. The second suction pipe 31b is also formed in another cylinder, adopting a configuration similar to that of the first suction pipe 31a. The suction muffler 60 is connected to the accumulator 300 by the low-pressure side piping 155b (see FIG. 8) of the refrigeration cycle circuit, and the refrigerant flows in from the accumulator 300. The suction muffler 60 is fixed to the outer periphery of the sealed container 3. The compressor 100 takes in the refrigerant (gas refrigerant) from the accumulator 300 through the first suction pipe 31a and the second suction pipe 31b into the sealed container 3. In addition, a discharge pipe 2a is connected to the upper part of the upper container 2 of the sealed container 3. The compressor 100 discharges the refrigerant compressed in the compression mechanism 10 to the outside via a discharge pipe 2a. The accumulator 300 will be described later.

<Compression mechanism 10>
The compression mechanism 10 is driven by the electric motor 20 and has a function of compressing the refrigerant.

The compression mechanism 10 includes a cylinder 13, a rolling piston 16, a bearing 14, a main shaft 11 and a vane (not shown).

The cylinder 13 is provided in the sealed container 3, has an outer periphery that is generally circular in plan view, and has a compression chamber 30, which is a generally circular space in plan view, inside. The cylinder 13 has a predetermined height in the axial direction when viewed from the side. The compression chamber 30 is open at both axial ends. The cylinder 13 is also provided with a vane groove (not shown) that communicates with the compression chamber 30 and extends radially, penetrating the cylinder 13 in the axial direction. The compression chamber 30 of the cylinder 13 is a space formed by attaching a bearing 14 and a partition plate 15 to the end of the cylindrical cylinder 13 in the direction of the main shaft 11. The refrigerant is compressed in the compression chamber 30.

The cylinder 13 is also provided with a suction port (not shown) through which the gas refrigerant sucked in through the first suction pipe 31a passes. The suction port is formed so as to penetrate from the outer circumferential surface of the cylinder 13 to the compression chamber 30.

The cylinder 13 is also provided with a discharge port (not shown) through which the refrigerant compressed in the compression chamber 30 is discharged from the compression chamber 30. The discharge port is formed by cutting out a part of the edge of the upper end surface of the cylinder 13.

The rolling piston 16 is formed in a ring shape and is housed in the compression chamber 30 so as to be capable of eccentric rotation. The rolling piston 16 is also fitted at its inner periphery to the eccentric shaft portion 12 of the main shaft 11 so as to be freely slidable.

A vane is housed in the vane groove (not shown). The vane housed in the vane groove is constantly pressed against the rolling piston 16 by a vane spring (not shown) provided in the back pressure chamber. The inside of the sealed container 3 of the compressor 100 is at high pressure, and when the compressor 100 starts operating, a force due to the pressure difference between the high pressure in the sealed container 3 and the pressure in the compression chamber 30 acts on the back pressure chamber on the back side of the vane. Therefore, the vane spring is mainly used to press the vane against the rolling piston 16 when the compressor 100 is started, when there is no difference in pressure between the sealed container 3 and the compression chamber 30.

The vane is shaped like a rectangular parallelepiped. Specifically, the vane has a flat, rectangular parallelepiped shape whose circumferential length (thickness) is smaller than its radial and axial lengths.

The bearing 14 is provided in the sealed container 3 and is configured in a generally inverted T-shape in side view. The bearing 14 is slidably fitted to the main shaft portion 11a, which is a portion above the eccentric shaft portion 12 of the main shaft 11. The bearing 14 closes one end face (the end face on the electric motor portion 20 side) of the compression chamber 30, which also includes the vane groove of the cylinder 13. The bearing 14 also has a discharge port 45 (see FIG. 2). The discharge port 45 is provided in the flange portion of the bearing 14 so that the compression chamber 30 and the sealed container 3 communicate with each other. The discharge port 45 is a hole that forms a passage through which the refrigerant passes when the refrigerant is discharged from the compression chamber 30 to the inside of the sealed container 3. The opening of the discharge port 45 on the compression chamber 30 side is provided on the end face of the compression chamber 30. Specifically, the opening of the discharge port 45 on the compression chamber 30 side is formed so as to be approximately in the same position in plan view as the discharge port on the upper surface of the compression chamber 30 formed in the cylinder 13. A discharge mechanism 40 having a valve body 41 (see FIGS. 2 and 3) is provided inside and above the bearing 14. The configuration of the discharge mechanism 40 will be described later. Note that the discharge mechanism 40 of the cylinder 13 provided with the second suction pipe 31b may be provided in the bearing 14a below the bearing 14.

The valve body 41 is adapted to open and close the discharge port 45 under the pressure in the compression chamber 30 and the pressure in the sealed container 3. When the pressure in the compression chamber 30 is lower than the pressure in the sealed container 3, the valve body 41 is pressed against the discharge port to close the discharge port 45. The valve body 41 is arranged so that when the valve body 41 closes the discharge port 45, the end face of the valve body 41 on the compression chamber 30 side does not cause any unevenness with respect to the end face of the discharge port 45 on the compression chamber 30 side. Therefore, the end face of the compression chamber 30 and the end face of the valve body 41 on the compression chamber 30 side are coincident on the same plane. In other words, the valve body 41 closes the opening face of the discharge port 45 on the compression chamber 30 side from the inside of the discharge port 45. Here, "coincidence" also includes the case where the end face of the valve body 41 on the compression chamber 30 side is only a short distance away from the end of the discharge port 45 to ensure clearance, etc. For example, the distance between the end face of the valve body 41 on the compression chamber 30 side and the end face of the compression chamber 30 is about one tenth of the total length of the discharge port 45. In order to increase the area that receives pressure from the compression chamber 30, the valve body 41 may have a recess, a groove, or the like formed on the compression chamber 30 side of the valve body 41.

On the other hand, when the pressure in the compression chamber 30 becomes higher than the pressure in the sealed container 3, the valve body 41 is pushed upward by the pressure in the compression chamber 30, opening the discharge port 45. When the discharge port 45 is opened, the refrigerant compressed in the compression chamber 30 is led to the outside of the compression chamber 30.

When the discharge port 45 opens, the high-temperature, high-pressure gas refrigerant discharged from the discharge port 45 is released into the sealed container 3.

The shape of the valve body 41 is, for example, cylindrical with an outer diameter Φ of 20 mm and a height of 16 mm.

An intake muffler 60 is provided next to the sealed container 3. The intake muffler 60 draws in low-pressure gas refrigerant from the refrigeration cycle. The intake muffler 60 prevents liquid refrigerant returning from the refrigeration cycle from being directly drawn into the compression chamber 30 of the cylinder 13. The intake muffler 60 is connected to the intake port of the cylinder 13 via a first intake pipe 31a and a second intake pipe 31b. The intake muffler 60 is fixed to the side of the sealed container 3 by welding or the like.

The high-temperature, high-pressure gas refrigerant compressed in the compression mechanism section 10 passes through the discharge port 45 (see Figure 2) of the discharge muffler 17, passes through the electric motor section 20, and is discharged from the discharge pipe 2a to the outside of the compressor 100.

<Motor section 20>
The electric motor unit 20 has a function of driving the compression mechanism unit 10 .

The electric motor section 20 is composed of a rotor 21, a stator 22, etc. The stator 22 is fixed in contact with the inner peripheral surface of the sealed container 3. The rotor 21 is arranged inside the stator 22 with a gap therebetween.

The stator 22 comprises at least a stator core made of multiple laminated electromagnetic steel sheets and a winding wound around the teeth of the stator core via an insulating material. Lead wires are connected to the windings of the stator 22. The lead wires are connected to glass terminals provided on the upper container 2 to supply power from outside the sealed container 3.

The rotor 21 includes at least a rotor core made of laminated electromagnetic steel sheets and a permanent magnet inserted into the rotor core. The main shaft portion 11a of the main shaft 11 is shrink-fitted or press-fitted into the center of the rotor core. An oil supply pump 70 is provided at the lower end of the main shaft 11, which is rotated by the electric motor portion 20. The oil supply pump 70 draws in the refrigeration oil that has accumulated in the sealed container 3 at the tip of the oil supply pump 70 by the centrifugal force generated by the rotation of the main shaft 11, and lifts it up by the centrifugal force. The refrigeration oil that has been drawn into the inside of the main shaft 11 and lifted up is supplied to the discharge mechanism 40 from the oil supply hole 11_1 (see FIG. 4) of the main shaft 11 provided in each part of the main shaft 11. In addition, the discharge muffler 17 is supplied with the refrigeration oil drawn into the main shaft 11 by the oil supply pump 70.

<Configuration of the discharge mechanism 40>
Fig. 2 is a diagram showing a state in which the valve body 41 of the discharge mechanism 40 of the compressor 100 according to the first embodiment closes the discharge port 45. Fig. 3 is a diagram showing a state in which the valve body 41 of the discharge mechanism 40 of the compressor 100 according to the first embodiment opens the discharge port 45. As shown in Figs. 2 and 3, the discharge mechanism 40 has the valve body 41, a spring 43, and a guide lid 46. In Fig. 2, the arrow indicates the high-pressure gas refrigerant that flows from the compression chamber 30 to the valve body 41. In Fig. 3, the arrow indicates the path of the high-pressure gas refrigerant.

The guide lid 46 has a cylindrical shape and has a blocking portion 46a provided on the upper side of the bearing 14 and a cylindrical portion 46b provided inside the bearing 14. The inside of the blocking portion 46a and the inside of the cylindrical portion 46b form the guide hole 42. The blocking portion 46a is a portion of the guide lid 46 on the side where the communication hole 44 is provided. The cylindrical portion 46b is a portion of the guide lid 46 on the side where the compression chamber 30 is provided, and is provided inside the bearing 14. The inside of the cylindrical portion 46b is connected to the discharge port 45. The lower end of the cylindrical portion 46b is formed to match the shape of the valve body 41, and the valve body seating portion 46c formed on the bearing 14 is disposed therein. The valve body seating portion 46c is chamfered. The chamfered surface is, for example, 2 mm in the height direction and 3 mm in the radial direction.

The blocking portion 46a and the cylindrical portion 46b of the guide lid 46 are formed as a single unit, but the blocking portion 46a and the cylindrical portion 46b may be formed as separate parts. The cylindrical portion 46b of the guide lid 46 is formed as a separate body from the bearing 14, but may be formed as a single unit. The bearing 14, the blocking portion 46a, and the cylindrical portion 46b are formed as two or three parts. One end of the spring 43, which is a connecting member, is attached to the blocking portion 46a of the guide lid 46. One end of the spring 43 is disposed in the guide hole 42 inside the guide lid 46. The other end of the spring 43 is attached to the valve body 41. The spring 43 exerts a spring force (elastic force) in the direction in which the valve body 41 closes the discharge port 45.

The guide hole 42 is a cylindrical space, and is inside the blocking portion 46a of the guide lid 46 and inside the cylindrical portion 46b of the guide lid 46. The cylindrical portion 46b is provided in a hole provided in the flange of the bearing 14. The end of the guide hole 42 on the compression chamber 30 side is formed so as to coincide with the end face of the compression chamber 30 and the inner wall of the cylinder 13. The lower portion of the bearing 14 coincides with the end face of the compression chamber 30 and the end face of the cylinder 13. The space inside the guide lid 46 may be formed by processing from the side of the flange of the bearing 14. The guide hole 42 may be formed by providing a fixing portion on the upper surface of the flange of the bearing 14 and covering the fixing portion with a member having a flat surface that acts as the guide hole 42. The end flat surface of the guide hole 42 on the opposite side to the compression chamber 30 may be formed by covering it with a separate part.

The gap between the side of the valve body 41 and the side of the guide hole 42 in the horizontal direction is less than 100 μm.

The end of the guide hole 42 on the compression chamber 30 side does not necessarily have to coincide with the end face of the compression chamber 30 provided below the guide hole 42 and the inner wall of the cylinder 13. For example, the position of the end of the guide hole 42 on the compression chamber 30 side may be located outside the inner wall of the cylinder 13. In this case, a part of the valve body 41 contacts, is close to, or contacts an elastic body arranged on the cylinder 13. In addition, the end of the guide hole 42 on the compression chamber 30 side may be located slightly inside the sealed container 3 than the end face of the compression chamber 30. This ensures clearance between the valve body 41 and the rolling piston 16.

In addition, when the guide lid 46 is a separate part from the bearing 14, the guide lid 46 may be provided inside the flange of the bearing 14. In this case, the length of the discharge port 45 is shortened, and the opening of the guide hole 42 on the compression chamber 30 side is made to be an opening that connects to the inside of the sealed container 3. The valve body seating portion 46c may be provided on the cylindrical portion 46b of the guide lid 46, instead of on the bearing 14.

When the discharge port 45 is opened widely, the tip of the valve body 41 may be in a state where it protrudes slightly into the inside of the discharge port 45 and partially covers the discharge port 45. This makes it possible to prevent the tip of the valve body 41 from entering inside the opening on the side of the discharge port 45.

A cylindrical communication hole 44 is formed in the blocking portion 46a of the guide lid 46. The communication hole 44 communicates between the guide hole 42 inside the guide lid 46 and the inside of the sealed container 3 where the high-pressure refrigerant discharged from the discharge port 45 is discharged through the discharge muffler 17. The horizontal outer diameter of the communication hole 44 is smaller than the horizontal outer diameter of the valve body 41. The diameter of the communication hole 44 is smaller than the inner diameter of the guide lid 46, and is Φ6 mm in this case. The shape of the communication hole 44 is circular, but an elliptical shape may be selected in consideration of interference with surrounding parts. The valve body seating portion 46c of the guide lid 46 may be formed in a shape in which at least a part of the bottom surface portion of the valve body 41 is exposed.

The valve body 41 is disposed in the guide hole 42, and when the pressure in the guide hole 42 is greater than the pressure in the compression chamber 30, it slides and moves downward along the guide hole 42. This closes the discharge port 45 (see FIG. 2). When the valve body 41 closes the discharge port 45, the side of the valve body 41 comes into contact with the side of the corresponding discharge port 45. Therefore, the side of the discharge port 45 of the valve body 41 is formed so that there is no unevenness with respect to the side of the discharge port 45. In addition, when the pressure in the guide hole 42 is less than the pressure in the compression chamber 30, the valve body 41 moves upward in the guide hole 42. This opens the discharge port 45 as shown in FIG. 3.

As shown in Figures 2 and 3, a discharge muffler 17 is provided around the discharge mechanism 40. The discharge muffler 17 is a component that occupies most of the sealed container 3 when the compressor 100 is viewed from above. When the compressor 100 is in operation, the refrigeration oil that has accumulated in the lower part of the sealed container 3 is rolled up, and the rolled up refrigeration oil accumulates in the upper part of the discharge muffler 17. An oil supply hole 17_1 of the discharge muffler 17 is provided at the upper part of the discharge muffler 17, above the communication hole 44. The refrigeration oil that has accumulated in the discharge muffler 17 is supplied from the oil supply hole 17_1 of the discharge muffler 17 to the communication hole 44. The oil supply is performed by dripping the refrigeration oil from the oil supply hole 17_1 of the discharge muffler 17 into the communication hole 44, but other methods may be used.

[Operation of Compressor 100]
Electric power is supplied to the stator 22 of the electric motor unit 20 via the lead wires. This causes current to flow through the windings of the stator 22, generating magnetic flux from the windings. The rotor 21 of the electric motor unit 20 rotates due to the interaction of the magnetic flux generated from the windings and the magnetic flux generated from the permanent magnets of the rotor 21. The rotation of the rotor 21 rotates the main shaft 11 fixed to the rotor 21. As the main shaft 11 rotates, the rolling piston 16 of the compression mechanism unit 10 rotates eccentrically within the compression chamber 30 of the cylinder 13.

The space between the cylinder 13 and the rolling piston 16 in the compression chamber 30 is divided into two by a vane (not shown). As the main shaft 11 rotates, the volumes of these two spaces change. In one space, the volume gradually expands and low-pressure gas refrigerant is sucked in from the accumulator 300. In the other space, the volume gradually decreases and the gas refrigerant inside is compressed in the compression chamber 30.

The gas refrigerant compressed in the compression chamber 30 and high in pressure and temperature pushes up the valve body 41 of the discharge mechanism 40 and is discharged from the discharge port 45. The vane (not shown) is pressed against the rolling piston 16 by the high-pressure refrigerant discharged into the sealed container 3, and slides radially in the vane groove in conjunction with the movement of the rolling piston 16, fulfilling the role of separating the low-pressure space of the compression chamber 30 from the high-pressure space. At this time, the discharge mechanism 40 opens and closes the discharge port 45 depending on the pressure difference between the discharge pressure in the sealed container 3 and the internal pressure of the compression chamber 30, and discharges the compressed refrigerant. The discharge pressure in the sealed container 3 changes depending on the operating conditions of the refrigeration cycle. For this reason, the discharge mechanism 40 opens and closes depending on the relative high and low of the discharge pressure in the sealed container 3, such as opening the valve body 41 when the pressure exceeds a predetermined pressure. The gas refrigerant discharged from the discharge port 45 is discharged into the space in the sealed container 3 through the discharge port 45 of the discharge muffler 17. The discharged gas refrigerant passes through a gap in the motor unit 20 and is discharged to the outside of the sealed container 3 from the discharge pipe 2a connected to the top of the sealed container 3. The refrigerant discharged to the outside of the sealed container 3 circulates through the refrigeration cycle and returns to the accumulator 300 again.

[Operation of the discharge mechanism 40]
Next, the operation of the discharge mechanism 40 will be described. First, when the internal pressure of the compression chamber 30 is lower than the internal pressure of the guide hole 42 of the discharge mechanism 40, the valve body 41 is loaded in a direction to close the discharge port 45 by the spring force of the spring 43 and the pressure in the guide hole 42. The end face of the valve body 41 on the compression chamber 30 side closes the discharge port 45 without protruding from the end face of the compression chamber 30, and receives the internal pressure of the compression chamber 30.

Next, the refrigerant is compressed in the compression chamber 30, and the end face of the valve body 41 facing the compression chamber 30 receives internal pressure. If the load caused by the internal pressure on the end face of the valve body 41 facing the compression chamber 30 is greater than the combined force of the internal pressure in the guide hole 42 of the discharge mechanism 40 and the spring force of the spring 43, the valve body 41, which had been blocking the discharge port 45, moves along the guide hole 42 toward the spring 43, as shown in Figure 3. Then, the valve body 41 opens the discharge port 45.

When the discharge port 45 opens, a discharge path for the refrigerant is formed. The high-temperature, high-pressure gas refrigerant discharged from the discharge port 45 is released into the sealed container 3. Specifically, the refrigerant passes through the inside of the guide hole 42 and the lower part of the valve body 41, passes through the flange of the bearing 14 (arrow a), passes through a hole provided on the side of the guide hole 42 (arrow b), and flows out into the inside of the discharge muffler 17. After that, the high-pressure refrigerant in the discharge muffler 17 passes through a gap formed between the bearing 14 and the discharge muffler 17 and a hole formed in the discharge muffler 17 itself (arrow c), and is discharged into the inside of the sealed container 3 of the compressor 100. When the discharge of the refrigerant is completed, the valve body 41 moves toward the discharge port 45 by the spring force of the spring 43 and begins to close the discharge port 45. Then, the internal pressure of the compression chamber 30 becomes smaller than the pressure in the sealed container 3. Next, as shown in FIG. 2, the tip of the valve body 41 on the compression chamber 30 side is pressed against the valve body seat portion 46c provided at the end of the discharge port 45 due to the pressure difference between the pressure in the guide hole 42 and the pressure in the compression chamber 30, and the discharge port 45 is completely closed.

When the compressor 100 is in operation, the oil supply pump 70 draws the refrigeration oil accumulated in the sealed container 3 up to the main shaft 11. The refrigeration oil drawn up to the main shaft 11 is fed to the discharge muffler 17 from the oil supply hole 11_1 (see FIG. 4) of the main shaft 11. The refrigeration oil fed to the discharge muffler 17 drips from the oil supply hole 17_1 of the discharge muffler 17 and is fed to the communication hole 44 provided below. The refrigeration oil fed to the communication hole 44 passes through the communication hole 44 and flows into the gap between the valve body 41 and the side of the guide hole 42.

The threshold value of the internal pressure of the compression chamber 30 where the refrigerant is discharged may be an absolute value. The spring 43 does not need to operate within the guide hole 42, and in order to reduce the pressure loss of the refrigerant passing through the communication hole 44, the spring 43 may be provided outside the guide hole 42, and the volume of the guide hole 42 may be expanded.

[effect]
According to the compressor 100 of the first embodiment, refrigeration oil is supplied to the communication hole 44. The refrigeration oil supplied to the communication hole 44 passes through the guide hole 42 and flows into the gap between the valve body 41 and the side surface of the guide hole 42. By covering the outer surface of the valve body 41 with refrigeration oil, the compressor 100 can suppress the occurrence of jamming of the valve body 41. This suppresses wear of the valve body 41 and makes it difficult for poor blocking of the compression chamber to occur, improving the efficiency of the compressor 100 and suppressing failures.

In addition, the gap between the side of the valve body 41 and the side of the guide hole 42 is less than 100 μm, and an oil level is formed between the side of the valve body 41 and the side of the guide hole 42 when the compressor 100 is in operation. This makes it possible to prevent jamming of the valve body 41. This improves the efficiency of the compressor 100 and prevents breakdowns.

Furthermore, according to the compressor 100 of the first embodiment, when the pressure in the guide hole 42 of the guide lid 46 is greater than the pressure in the compression chamber 30, the valve body 41 moves inside the guide hole 42 and the discharge port 45 is closed. The refrigerant discharged from the discharge port 45 is discharged into the sealed container 3. Since the communication hole 44 is connected to the space inside the sealed container 3, the space inside the guide hole 42 and above the valve body 41 is compressed by the discharged refrigerant, which has a higher pressure than the refrigerant retained in the guide hole 42, and the damper effect suppresses the delay in closing the discharge port 45 by the valve body 41.

Furthermore, according to the compressor 100 of the first embodiment, a communication hole 44 is provided in the guide lid 46. The diameter of the communication hole 44 is smaller than the inner diameter of the guide lid 46. Therefore, when the valve body 41 rises, the refrigerant in the space between the valve body 41 and the blocking portion 46a does not escape through the communication hole 44, and the refrigerant is compressed and the valve body 41 is pushed back. At this time, the pressure of the refrigerant remaining in the space between the valve body 41 and the blocking portion 46a is higher than the high-pressure refrigerant discharged into the sealed container 3 after the compression process is completed. Due to this damper effect, the valve body 41 starts to descend quickly after the completion of the rise, and seats on the valve body seating portion 46c provided in the bearing 14 without closing late from the desired seating timing.

Furthermore, according to the compressor 100 of embodiment 1, the horizontal outer diameter of the communication hole 44 is made smaller than the horizontal outer diameter of the valve body 41, thereby further preventing a decrease in the closing speed of the valve body 41.

Furthermore, according to the compressor 100 of embodiment 1, the end of the guide hole 42 on the compression chamber 30 side is formed to coincide with the end face of the compression chamber 30 and the inner wall of the cylinder 13, thereby increasing the flow path area of the refrigerant and reducing the discharge pressure loss.

Furthermore, according to the compressor 100 of the first embodiment, the discharge path is configured to have the compression chamber 30, the valve body 41, and the discharge port 45 in that order. Then, immediately after the compression chamber 30, the valve body 41 closes the discharge port 45. This makes it possible to reduce the dead volume of the compressor 100. This makes it possible to suppress a decrease in the efficiency of the compressor 100 due to re-expansion of the refrigerant.

Furthermore, according to the compressor 100 of the first embodiment, the end face of the compression chamber 30 and the end face of the valve body 41 on the compression chamber 30 side are aligned on the same plane. This makes it possible to minimize the dead volume of the compressor 100, and to prevent the valve body 41 from protruding into the compression chamber 30 and colliding with the rolling piston 16.

Furthermore, according to the compressor 100 of embodiment 1, the cylindrical portion 46b of the guide cover 46 is formed as a separate part from the bearing 14, so that the structure of the bearing 14 can be simplified and a low-cost compressor 100 can be provided.

Furthermore, according to the compressor 100 of embodiment 1, when the cylindrical portion 46b of the guide cover 46 is integrally formed with the bearing 14, misalignment between the valve body 41 and the valve body seating portion 46c can be suppressed, thereby providing a highly reliable compressor 100.

The bearing 14 has a sliding portion with the main shaft 11 and the rolling piston 16, and distortion of several to several tens of μm occurs. This distortion adversely affects the reliability of the compressor 100. Specifically, at the distortion location, metal parts come into local contact with each other, causing seizure. According to the compressor 100 of embodiment 1, the guide lid 46 may be fixed to the bearing 14 by screws. In this case, the force applied to the bearing 14 during assembly of the compressor 100 is reduced, and distortion occurring in the bearing 14 can be reduced.

Furthermore, according to the compressor 100 of the first embodiment, the horizontal outer diameter of the communication hole 44 is smaller than the horizontal outer diameter of the valve body 41. This allows the communication hole 44 to act as a throttle portion, and has the effect of not suppressing the damping effect that the communication hole 44 was intended to suppress more than the design desires. In addition, this has the effect of helping the valve body 41 close quickly when the discharge port 45 is closed.

Embodiment 2.
In the second embodiment, the method of supplying oil to the communication hole 44 of the discharge mechanism 40 is different from that in the first embodiment. Fig. 4 is a diagram for explaining the method of supplying oil to the communication hole 44 of the discharge mechanism 40 of the compressor 100 according to the second embodiment. In Fig. 4, the same parts as those in Figs. 1 to 3 will be described with the same reference numerals.

As shown in FIG. 4, the main shaft 11 is provided with an oil supply hole 11_1 for discharging refrigeration oil. The discharge muffler 17 also serves as a guide lid 46, and has a communication hole 44 formed therein. The communication hole 44 is provided at a lower position than the oil supply hole 11_1 of the main shaft 11. The discharge muffler 17 has an oil reservoir 17_2 provided above the communication hole 44. The oil reservoir 17_2 is formed by the discharge muffler 17, and is formed in a box shape so that refrigeration oil can be stored therein, but may be of another shape. The communication hole 44 is formed in the lower part of the oil reservoir 17_2.

Refrigeration oil flowing out from the oil supply hole 11_1 of the main shaft 11 flows along the surface of the discharge muffler 17 and is stored in the oil reservoir 17_2. The refrigeration oil stored in the oil reservoir 17_2 passes through the communication hole 44 and flows into the gap between the valve body 41 and the side of the guide hole 42.

Therefore, according to the compressor 100 of the second embodiment, the communication hole 44 is provided at a position lower than the position of the oil supply hole 11-1 of the main shaft 11, so that the refrigeration oil flowing out from the oil supply hole 11-1 of the main shaft 11 flows along the surface of the discharge muffler 17 and is stored in the oil reservoir 17_2. This allows the refrigeration oil to be constantly supplied to the discharge mechanism 40.

In addition, according to the compressor 100 of the second embodiment, the discharge muffler 17 has a communication hole 44, so that the discharge muffler 17 can also serve as the guide lid 46. Therefore, the number of parts of the compressor 100 can be reduced, and a low-cost compressor 100 can be provided.

Embodiment 3.
In the third embodiment, the method of supplying oil to the communication hole 44 of the discharge mechanism 40 is different from that in the first and second embodiments. Fig. 5 is a diagram for explaining the method of supplying oil to the communication hole 44 of the discharge mechanism 40 of the compressor 100 according to the third embodiment. In Fig. 5, the same parts as those in Figs. 1 to 4 will be described with the same reference numerals.

Figure 5 differs from Figure 3 in that an oil supply pipe 18 is provided that connects the oil supply hole 17_1 of the discharge muffler 17 to the communication hole 44. Also, an oil reservoir 17_2 is provided on the upper surface of the discharge muffler 17 in this embodiment. The space surrounded by a wall provided around the oil supply hole 17_1 is the oil reservoir 17_2 in this embodiment.

When the compressor 100 is in operation, the oil supply pump 70 draws the refrigeration oil accumulated in the sealed container 3 up to the main shaft 11. The refrigeration oil drawn up to the main shaft 11 is fed to the discharge muffler 17 from the oil supply hole 11_1 (see FIG. 4) of the main shaft 11. The refrigeration oil fed to the discharge muffler 17 accumulates in the oil reservoir 17_2 of the discharge muffler 17. The refrigeration oil accumulated in the oil reservoir 17_2 passes through the oil supply hole 17_1 and the oil supply pipe 18 in sequence, and is fed to the communication hole 44 provided below. The refrigeration oil fed to the communication hole 44 passes through the communication hole 44 and flows into the gap between the valve body 41 and the side of the guide hole 42.

According to the compressor 100 of the third embodiment, when the compressor 100 is in operation, the oil supply pump 70 draws the refrigeration oil accumulated in the sealed container 3 up to the main shaft 11. The refrigeration oil drawn up to the main shaft 11 is fed to the discharge muffler 17 from the oil supply hole 11_1 of the main shaft 11. The refrigeration oil fed to the discharge muffler 17 flows from the oil supply hole 17_1 of the discharge muffler 17 to accumulate in the oil reservoir 17_2. The refrigeration oil accumulated in the oil reservoir 17_2 is fed from the oil supply hole 17_1 of the discharge muffler 17 to the communication hole 44 through the oil supply pipe 18.

Therefore, according to the compressor 100 of embodiment 3, refrigeration oil is supplied from the oil reservoir 17_2 of the discharge muffler 17 through the oil supply pipe 18 to the communication hole 44, so that the refrigeration oil can be supplied to the discharge mechanism 40 without being obstructed by the turbulent fluid in the discharge muffler 17.

Embodiment 4.
Fig. 6 is a diagram showing a linear oil supply groove 81 provided in the discharge mechanism 40 of the compressor 100 according to the fourth embodiment. Specifically, as shown in Fig. 6, the oil supply groove 81 is formed linearly along the vertical direction on the inner surfaces of the closing portion 46a and the cylindrical portion 46b of the guide lid 46. The oil supply groove 81 does not extend to the valve body seating portion 46c. The oil supply groove 81 has a width of 2 mm and a height of 4 mm, for example.

The oil groove 81 is not limited to a linear oil groove 81. Figure 7 is a diagram showing a spiral oil groove 81_1 provided in the discharge mechanism 40 of the compressor 100 according to embodiment 4.

Refrigeration oil supplied to the communication hole 44 is supplied to the oil supply groove 81 or the oil supply groove 81_1.

Therefore, according to the compressor 100 of embodiment 4, refrigeration oil is supplied to the oil supply groove 81 or the oil supply groove 81_1, thereby further suppressing jamming of the valve body 41.

Embodiment 5.
Fig. 8 is a refrigerant circuit diagram that shows a schematic refrigerant circuit configuration of a refrigeration cycle apparatus 200 according to embodiment 5. The configuration and operation of the refrigeration cycle apparatus 200 will be described with reference to Fig. 8. The refrigeration cycle apparatus 200 according to embodiment 5 includes any one of the compressors 100 according to embodiments 1 to 3 as an element of the refrigerant circuit. For convenience, Fig. 8 shows a case where the compressor 100 according to embodiment 1 is included.
<Configuration of refrigeration cycle device 200>
The refrigeration cycle apparatus 200 includes a compressor 100, a flow switching device 151, a first heat exchanger 152, an expansion device 153, and a second heat exchanger 154. The compressor 100, the first heat exchanger 152, the expansion device 153, and the second heat exchanger 154 are connected by a high-pressure side pipe 155a and a low-pressure side pipe 155b to form a refrigerant circuit. An accumulator 300 is disposed upstream of the compressor 100.

The compressor 100 compresses the sucked refrigerant to a high temperature and high pressure state. The refrigerant compressed by the compressor 100 is discharged from the compressor 100 and sent to the first heat exchanger 152 or the second heat exchanger 154.

The flow path switching device 151 switches the flow of refrigerant between heating operation and cooling operation. That is, the flow path switching device 151 is switched to connect the compressor 100 and the second heat exchanger 154 during heating operation, and is switched to connect the compressor 100 and the first heat exchanger 152 during cooling operation. The flow path switching device 151 may be configured, for example, as a four-way valve. However, a combination of two-way or three-way valves may also be used as the flow path switching device 151.

The first heat exchanger 152 functions as an evaporator during heating operation and as a condenser during cooling operation. That is, when functioning as an evaporator, the first heat exchanger 152 exchanges heat between the low-temperature, low-pressure refrigerant discharged from the expansion device 153 and air supplied by, for example, a blower (not shown), and the low-temperature, low-pressure liquid refrigerant (or gas-liquid two-phase refrigerant) evaporates. On the other hand, when functioning as a condenser, the first heat exchanger 152 exchanges heat between the high-temperature, high-pressure refrigerant discharged from the compressor 100 and air supplied by, for example, a blower (not shown), and the high-temperature, high-pressure gas refrigerant condenses. The first heat exchanger 152 may be configured as a refrigerant-water heat exchanger. In this case, the first heat exchanger 152 exchanges heat between the refrigerant and a heat medium such as water.

The expansion device 153 expands and reduces the pressure of the refrigerant flowing out of the first heat exchanger 152 or the second heat exchanger 154. The expansion device 153 may be, for example, an electric expansion valve capable of adjusting the flow rate of the refrigerant. Note that the expansion device 153 may be not only an electric expansion valve, but also a mechanical expansion valve using a diaphragm in the pressure receiving section, or a capillary tube.

The second heat exchanger 154 functions as a condenser during heating operation and as an evaporator during cooling operation. That is, when functioning as a condenser, the second heat exchanger 154 exchanges heat between the high-temperature, high-pressure refrigerant discharged from the compressor 100 and air supplied by, for example, a blower (not shown), and the high-temperature, high-pressure gas refrigerant is condensed. On the other hand, when functioning as an evaporator, the second heat exchanger 154 exchanges heat between the low-temperature, low-pressure refrigerant discharged from the expansion device 153 and air supplied by, for example, a blower (not shown), and the low-temperature, low-pressure liquid refrigerant (or gas-liquid two-phase refrigerant) evaporates. The second heat exchanger 154 may be configured as a refrigerant-water heat exchanger. In this case, the second heat exchanger 154 exchanges heat between the refrigerant and a heat medium such as water.

The refrigeration cycle apparatus 200 is also provided with a control device 160 that performs overall control of the refrigeration cycle apparatus 200. Specifically, the control device 160 controls the drive frequency of the compressor 100 according to the required cooling or heating capacity. The control device 160 also controls the opening degree of the expansion device 153 according to the operating state and each mode. Furthermore, the control device 160 controls the flow path switching device 151 according to each mode.

Based on operating instructions from the user, the control device 160 uses information sent from each temperature sensor and each pressure sensor (not shown) to control each actuator, such as the compressor 100, the expansion device 153, the flow path switching device 151, etc.

The control device 160 may be configured with hardware such as a circuit device that realizes its functions, or may be configured with a computing device such as a microcontroller or CPU and software executed on it.

The control device 160 is composed of dedicated hardware or a CPU (also called a central processing unit, processing device, arithmetic device, microprocessor, microcomputer, or processor) that executes a program stored in memory. When the control device 160 is dedicated hardware, the control device 160 is, for example, a single circuit, a composite circuit, an ASIC (Application Specific Integrated Circuit), an FPGA (Field Programmable Gate Array), or a combination of these. Each of the functional units realized by the control device 160 may be realized by individual hardware, or each functional unit may be realized by a single piece of hardware. When the control device 160 is a CPU, each function executed by the control device 160 is realized by software, firmware, or a combination of software and firmware. The software and firmware are written as programs and stored in memory. The CPU reads out and executes programs stored in the memory to realize each function of the control device 160. Here, the memory is, for example, a non-volatile or volatile semiconductor memory such as a RAM, a ROM, a flash memory, an EPROM, an EEPROM, etc. Note that some of the functions of the control device 160 may be realized by dedicated hardware, and some may be realized by software or firmware.

<Operation of the refrigeration cycle device 200>
Next, the operation of the refrigeration cycle apparatus 200 will be described together with the flow of the refrigerant. Here, the operation of the refrigeration cycle apparatus 200 during cooling operation will be described using an example in which the heat exchange fluid in the first heat exchanger 152 and the second heat exchanger 154 is air. In addition, in Fig. 8, the flow of the refrigerant during cooling operation is indicated by dashed arrows, and the flow of the refrigerant during heating operation is indicated by solid arrows.

By driving the compressor 100, a high-temperature, high-pressure gaseous refrigerant is discharged from the compressor 100. The high-temperature, high-pressure gas refrigerant (single phase) discharged from the compressor 100 flows into the first heat exchanger 152. In the first heat exchanger 152, heat exchange takes place between the high-temperature, high-pressure gas refrigerant that has flowed in and air supplied by a blower (not shown), and the high-temperature, high-pressure gas refrigerant condenses to become a high-pressure liquid refrigerant (single phase).

The high-pressure liquid refrigerant sent out from the first heat exchanger 152 is converted by the expansion device 153 into a two-phase refrigerant of low-pressure gas refrigerant and liquid refrigerant. The two-phase refrigerant flows into the second heat exchanger 154. In the second heat exchanger 154, heat is exchanged between the two-phase refrigerant that has flowed in and the air supplied by a blower (not shown), and the liquid refrigerant in the two-phase refrigerant evaporates and becomes a low-pressure gas refrigerant (single phase). The low-pressure gas refrigerant sent out from the second heat exchanger 154 flows into the compressor 100 via the accumulator 300, is compressed into a high-temperature, high-pressure gas refrigerant, and is discharged from the compressor 100 again. This cycle is repeated.

Therefore, according to the refrigeration cycle device 200 of embodiment 5, it is possible to provide a refrigeration cycle device 200 using a compressor 100 with good compression efficiency.

In addition, the operation of the refrigeration cycle device 200 during heating operation is carried out by the flow path switching device 151 changing the flow of refrigerant to the flow indicated by the solid arrows in Figure 8.

In addition, the flow of refrigerant may be in a fixed direction without providing a flow path switching device 151 on the discharge side of the compressor 100.

In addition, the refrigerant used in the refrigeration cycle device 200 is not particularly limited, and refrigerants such as carbon dioxide, R410A, R32, and HFO1234yf can be used.

Furthermore, application examples of the refrigeration cycle device 200 include air conditioning devices, water heaters, refrigerators, or combined air conditioning and hot water supply devices.

Embodiment 6.
In the sixth embodiment, the type of refrigerant used in the refrigeration cycle apparatus 200 of the fourth embodiment will be described.

The refrigerant used in the refrigeration cycle device 200 of the sixth embodiment is a refrigerant with a lower gas density than the R410A refrigerant. For example, R134a, R1234yf, R513A, R463A, R290, R454C, R454A, R404A, R448A, R449A, R454B, R452B, R466A, etc.

Figure 9 is a diagram showing the gas density of the refrigerant sucked into the compressor and the gas density of the refrigerant discharged from the compressor for each refrigerant at the rated compressor operating conditions of a typical refrigeration cycle specified in ASHRAE.

Here, ASHRAE is an abbreviation for the American Society of Heating, Refrigerating and Air-Conditioning Engineers. The rated operating conditions of the compressor are commonly known as ASRAE-T conditions, and are a condensing temperature of 54.4°C, an evaporating temperature of 7.2°C, a degree of subcooling of 8.3°C, and a degree of superheat of 27.8°C.

In Figure 9, the following refrigerants are shown: R134a, R1234yf, R513A, R463A, R290, R454C, R454A, R404A, R448A, R449A, R454B, R452B, and R466A. As shown in Figure 9, the gas density of these refrigerants, sucked into the compressor and discharged from the compressor, is lower than that of R410A.

Generally, pressure loss of fluids such as refrigerant gas increases in proportion to the flow rate of the fluid. When circulating the same weight of refrigerant, the gas flow rate needs to be faster as the density decreases. In other words, low-density refrigerant gas will experience greater pressure loss than high-density refrigerant gas. This pressure loss occurs in various places in the refrigeration cycle, but its effects are particularly noticeable in places where the flow path is narrow and the fluid flow rate is fast, such as the compression discharge valve.

Pressure loss in the flow path results in energy loss, which reduces the efficiency of the entire refrigeration cycle. Reed valves are generally used as discharge valves in rotary compressors. Figure 10 is a diagram showing an example of a reed valve of a compressor. As shown in Figure 10, one end of a reed valve 401 and a regulating plate 402 are fixed by a fixing rivet 403 near a discharge hole 405 provided on the end face of the bearing 14. The regulating plate 402 regulates the movement of the reed valve. The reed valve 401 sits on a seating portion 404 and blocks the discharge hole 405. The reed valve 401 is lifted by an increase in pressure in the compression chamber 30. As described above, since the reed valve 401 has a cantilever structure, the lift distance R of the fixed portion side of the reed valve 401 from the end face of the bearing 14 is reduced, and the overall flow path area is reduced.

11 is a diagram for explaining the lift distance R of the valve body 41 of the compressor 100 used in the refrigeration cycle device 200 of embodiment 6. As shown in Fig. 11, the valve body 41 of the discharge mechanism 40 of the compressor 100 moves vertically in the guide hole 42 by the spring 43. Therefore, the lift distance R is uniform over the entire valve body 41, and the overall refrigerant flow path area is larger than that of the reed valve 401.

By increasing the flow area of the refrigerant, the flow velocity at the discharge port 45 decreases, and the pressure loss at the discharge port 45 decreases. This effect is more noticeable with refrigerants that have a low gas density.

The refrigeration cycle device 200 of the sixth embodiment applies a refrigerant having a lower gas density than R410A, which is currently widely used around the world, to the refrigeration cycle device 200 of the fourth embodiment. Therefore, the refrigeration cycle device 200 of the sixth embodiment can reduce pressure loss and obtain a highly efficient refrigeration cycle. In particular, when R290 is used as the refrigerant, the intake gas density and discharge gas density are significantly higher than those of other refrigerants, so that the refrigeration cycle device 200 can reduce pressure loss and obtain a highly efficient refrigeration cycle.

The embodiments are presented as examples and are not intended to limit the scope of the claims. The embodiments may be implemented in various other forms, and various omissions, substitutions, and modifications may be made without departing from the gist of the embodiments. These embodiments and their variations are included within the scope and gist of the embodiments.

1 Lower container, 2 Upper container, 2a Discharge pipe, 3 Sealed container, 10 Compression mechanism, 11 Main shaft, 11a Main shaft, 11_1 Oil supply hole of main shaft 11, 12 Eccentric shaft, 13 Cylinder, 14, 14a Bearing, 15 Partition plate, 16 Rolling piston, 17 Discharge muffler, 17_1 Oil supply hole of discharge muffler 17, 17_2 Oil reservoir, 18 Oil supply pipe, 20 Motor, 21 Rotor, 22 Stator, 30 Compression chamber, 31a First intake pipe, 31b Second intake pipe, 40 Discharge mechanism, 41 Valve body, 42 Guide hole, 43 Spring, 44 Communication hole, 45 Discharge port, 46 Guide lid, 46a Blocking portion, 46b Cylindrical portion, 46c Valve body seating portion, 50 Intake port, 60 Intake muffler, 70 oil supply pump, 81, 81_1 oil supply groove, 100 compressor, 151 flow path switching device, 152 first heat exchanger, 153 expansion device, 154 second heat exchanger, 155a high pressure side piping, 155b low pressure side piping, 160 control device, 200 refrigeration cycle device, 300 accumulator, 401 reed valve, 402 regulating plate, 403 fixing rivet, 404 seating portion, 405 discharge hole, R lift distance.

Claims (10)

A sealed container;
a cylinder provided within the sealed container and having a compression chamber therein in which a refrigerant is compressed;
A main shaft provided in the sealed container;
a bearing provided on the main shaft and having a discharge port for discharging the refrigerant compressed in the compression chamber;
a discharge mechanism including a guide cover provided on the bearing and having a guide hole therein, and a valve body provided in the guide hole, the valve body moving within the guide hole to open and close the discharge port,
a communication hole is formed in the guide lid, the communication hole communicating the guide hole with the inside of the sealed container into which the refrigerant discharged from the discharge port is discharged;
The compressor is supplied with refrigeration oil retained in the sealed container through the communication hole. an oil supply pump provided at a lower end of the main shaft and configured to draw refrigeration oil remaining in the sealed container into the main shaft;
a discharge muffler to which the refrigeration oil drawn into the main shaft by the oil supply pump is supplied,
The compressor according to claim 1 , wherein the discharge muffler is formed with an oil supply hole for supplying the refrigeration oil to the communication hole. The discharge muffler is
3. The compressor according to claim 2, further comprising an oil reservoir provided above said oil supply hole. The main shaft is provided with an oil supply hole for discharging the refrigeration oil,
The compressor according to any one of claims 1 to 3, wherein the communication hole is provided at a position lower than a position of the oil supply hole of the main shaft . 4. The compressor according to claim 2, further comprising an oil supply pipe communicating between an oil supply hole of the discharge muffler and the communication hole. The compressor according to any one of claims 1 to 5, wherein a groove is formed on the horizontal side of the guide lid on the guide hole side, through which the refrigeration oil is supplied from the communication hole. The compressor according to any one of claims 1 to 6, wherein the gap between the side of the valve body and the side of the guide hole in the horizontal direction is less than 100 μm. A refrigeration cycle device comprising the compressor according to any one of claims 1 to 7, and a refrigerant circulating sequentially through a first heat exchanger, an expansion device, and a second heat exchanger. The refrigeration cycle device according to claim 8, wherein the refrigerant has a lower gas density than R410A. The refrigeration cycle device according to claim 9, wherein the refrigerant is R290.

Images