WO2019186800A1

WO2019186800A1 - Hermetic compressor and refrigeration cycle device

Info

Publication number: WO2019186800A1
Application number: PCT/JP2018/012883
Authority: WO
Inventors: 貴也木本; 将吾諸江; 英人中尾; 関屋　慎; 角田　昌之
Original assignee: 三菱電機株式会社
Priority date: 2018-03-28
Filing date: 2018-03-28
Publication date: 2019-10-03
Also published as: JPWO2019186800A1; JP6556372B1

Abstract

This hermetic compressor is provided with: a hermetic container serving as an outer shell; a compression mechanism installed within the hermetic container and compressing, within a compression chamber, a sucked-in fluid; a discharge opening which is a passage through which the fluid compressed by the compression mechanism is discharged from the compression chamber into the hermetic container; and a discharge mechanism having a valve body which opens and closes the discharge opening, the valve body being operated by the pressure difference between inner pressure in the compression chamber and pressure in the hermetic container. The discharge mechanism is disposed at a position where the valve body closes the compression chamber-side open face of the discharge opening when the valve body moves in a direction intersecting the center axis of the discharge opening and closes the discharge opening.

Description

Hermetic compressor and refrigeration cycle apparatus

The present invention relates to a hermetic compressor and a refrigeration cycle apparatus. In particular, the present invention relates to a reed valve that opens and closes a compression chamber.

Conventionally, a reed valve is provided at the discharge port of the hermetic compressor. When the compression chamber reaches a predetermined pressure, the valve body opens, and when the refrigerant in the compression chamber is discharged, the discharge port is closed by the spring force of the reed valve. Here, since the discharge port has a certain thickness, the high-pressure refrigerant stays in the volume of the discharge port, that is, the so-called dead volume. There was a problem that the efficiency of the compressor was reduced by the re-expansion of the accumulated refrigerant in the compression chamber. On the other hand, there is a compressor in which the tip of the reed valve is a tapered protrusion, and the discharge port is formed in a tapered shape to reduce the dead volume (see, for example, Patent Document 1). .

Japanese Patent Laid-Open No. 2005-188421

In the case of a compressor in which the discharge port is tapered to reduce the dead volume, the tapered shape of the valve body may narrow the flow path of the discharge port and increase the discharge pressure loss. Therefore, if the taper angle is increased in order to reduce the discharge pressure loss, it is necessary to reduce the thickness of the discharge port. At this time, since the valve body opens and closes in the direction of the thin wall, the discharge port easily deforms to the compression chamber side due to the slamming of the valve body, the pressure difference, and the like, and there is a possibility that the piston in the compression chamber may be burned. Further, in the case of a compressor in which a protrusion is provided at the tip of the reed valve, there is a problem that stress concentration occurs at the bent portion and the reed valve is easily damaged.

In order to solve the above-described problems, an object of the present invention is to provide a hermetic compressor and a refrigeration cycle apparatus capable of reducing dead volume and improving efficiency without having a tapered discharge port. To do.

A hermetic compressor according to the present invention includes a hermetic container serving as an outer shell, a compression mechanism that is installed in the hermetic container and compresses the sucked fluid in the compression chamber, and the fluid compressed by the compression mechanism is the compression chamber. A discharge port that is a passage for discharging from the inside of the closed container to the inside of the sealed container and a valve body that opens and closes the discharge port, and the valve body is operated by the pressure difference between the internal pressure of the compression chamber and the pressure in the sealed container. The discharge mechanism is arranged at a position where the valve body moves in a direction intersecting the central axis of the discharge port, and when the valve body closes the discharge port, the opening surface on the compression chamber side of the discharge port is closed. It is what is done.

Also, the refrigeration cycle apparatus according to the present invention has a refrigerant circuit in which a hermetic compressor, a condenser, a decompression device, and an evaporator are connected by piping to circulate the refrigerant.

According to the present invention, since the valve body opens and closes the discharge port at the opening on the compression chamber side, the dead volume can be reduced, the re-expansion of the fluid is suppressed, and the efficiency of the compressor is increased. Can be improved.

It is a figure explaining the structure of the hermetic compressor which concerns on Embodiment 1 of this invention. It is a figure explaining the structure of the discharge mechanism 40 in the bearing 14 which concerns on Embodiment 1 of this invention. It is a figure which shows the mode of the discharge mechanism 40 seen from the angle different from FIG. It is a figure which shows operation | movement of the discharge mechanism 40 which concerns on Embodiment 1 of this invention. It is a figure which shows the ratio of the opening of the discharge port 45 with respect to the installation angle of the valve body 41 concerning Embodiment 1 of this invention, and the ratio of the fluid force which acts on the valve body 41. FIG. It is a figure explaining the structure of the discharge mechanism 40 in the rotary compressor 100 which concerns on Embodiment 2 of this invention. It is a figure explaining the structure of the discharge mechanism 40 of the rotary compressor 100 which concerns on Embodiment 3 of this invention. It is a figure showing the structural example of the refrigerating-cycle apparatus which concerns on Embodiment 4 of this invention.

Hereinafter, a compressor and a refrigeration cycle apparatus according to an embodiment of the invention will be described with reference to the drawings. In the following drawings, the same reference numerals denote the same or corresponding parts, and are common to the whole text of the embodiments described below. In the drawings, the size relationship of each component may be different from the actual one. And the form of the component represented by the whole specification is an illustration to the last, Comprising: It does not limit to the form described in the specification. In particular, the combination of the components is not limited to the combination in each embodiment, and the components described in the other embodiments can be applied to another embodiment. Further, the pressure and temperature levels are not particularly determined in relation to absolute values, but are relatively determined in the state and operation of the apparatus. In the following description, the longitudinal direction (vertical direction in the figure) of the sealed container 1 is defined as the axial direction, and the direction passing through the central axis of the sealed container 1 and perpendicular to the central axis is described as the radial direction.

Embodiment 1 FIG.
FIG. 1 is a diagram illustrating the configuration of a hermetic compressor according to Embodiment 1 of the present invention. Here, the rotary compressor 100 will be described as an example of a hermetic compressor. However, the present invention can also be applied to a hermetic compressor having a discharge valve, such as a scroll compressor or a reciprocating compressor. Here, the description will be made assuming that the fluid compressed by the rotary compressor 100 is a refrigerant used in a refrigeration cycle apparatus or the like.

The rotary compressor 100 includes a compression mechanism unit 10, a rotor 21, and a stator 22, and an electric motor unit 20 that drives the compression mechanism unit 10 via a main shaft 11 inside the hermetic container 1 serving as an outer shell. It has. The compression mechanism unit 10 includes an eccentric shaft unit 12 that rotates together with the main shaft 11, a cylinder 13, a bearing 14, and a partition plate 15. The compression chamber 30 is a space formed by attaching the bearing 14 and the partition plate 15 to the axial end of the cylindrical cylinder 13. A piston 16 and a vane (not shown) that are slidably fitted to the eccentric shaft portion 12 are disposed in the compression chamber 30. A radial vane groove (not shown) is formed in the cylinder 13. The vane groove slidably holds the vane. The back side of the vane is open to the space of the sealed container 1. The cylinder 13 is formed with a radial suction port 50. The cylinder 13 guides the refrigerant sucked from the suction muffler 60 to the compression chamber 30. The refrigerant compressed in the compression chamber 30 is discharged from the compression chamber 30 into the sealed container 1 via the discharge mechanism 40.

FIG. 2 is a view for explaining the configuration of the discharge mechanism 40 in the bearing 14 according to Embodiment 1 of the present invention. FIG. 3 is a view showing a state of the discharge mechanism 40 viewed from an angle different from that in FIG. The valve body 41, the guide hole 42, and the bearing 14 in FIG. 3 are shown in a cross-sectional view taken along the AA plane shown in FIG. The bearing 14 includes a discharge mechanism 40. In the compression chamber 30, the internal pressure increases and decreases by the operation of the piston 16. The discharge mechanism 40 operates with a pressure difference between the internal pressure of the compression chamber 30 and the internal pressure of the sealed container 1. The discharge mechanism 40 prevents the fluid from being discharged from the compression chamber 30 into the sealed container 1 when the internal pressure of the compression chamber 30 is low, and discharges the fluid when the internal pressure of the compression chamber 30 becomes high. Note that the threshold value of the internal pressure of the compression chamber 30 to be discharged may be an absolute value, but may be determined depending on the relative level as will be described later.

The discharge mechanism 40 in the first embodiment includes a valve body 41, a guide hole 42, a spring material 43, a communication hole 44, and a discharge port 45. The discharge port 45 is provided in the flange portion of the bearing 14 so that the compression chamber 30 and the sealed container 1 communicate with each other. When the refrigerant is discharged from the compression chamber 30 into the sealed container 1, the discharge port 45 is a passage through which the refrigerant passes. An opening of the discharge port 45 on the compression chamber 30 side is provided on the end surface of the compression chamber 30. In addition, a central axis 45a is formed at the discharge port 45 so as to follow the direction in which the refrigerant flows. The guide hole 42 is a through hole in which a flat wall having an angle α of 45 ° or less is formed in the flange portion of the bearing 14 between the opening surface of the discharge port 45 (end surface of the compression chamber 30). One of the guide holes 42 opens into the discharge port 45 and communicates with the discharge port 45. The valve body 41 is installed in the guide hole 42, and can reciprocate along the guide hole 42 slidably in a direction intersecting the central axis 45 a of the discharge port 45. That is, the guide hole 42 is a guide for moving in a direction in which the valve body 41 intersects. Further, when the valve body 41 closes the discharge port 45, the end surface on the discharge port 45 side of the valve body 41 is in line contact with the side surface of the opposite discharge port 45 as shown by the dotted line in FIG. And as shown in FIG. 2, it forms so that an unevenness | corrugation may be eliminated with respect to the end surface of the compression chamber 30. FIG. The spring material 43, which is an elastic body, is installed on the opposite surface of the valve body 41 on the discharge port 45 side. The spring material 43 gives a spring force (elastic force) in a direction in which the valve body 41 closes the discharge port 45. The communication hole 44 is provided so as to communicate the space in which the spring material 43 is stored and the inside of the sealed container 1. In addition, there is no designation | designated in the shape of the communicating hole 44, For example, it is good also as a structure etc. which open | released the space which the spring material 43 accommodates widely in the airtight container 1 inside.

Next, the operation of the rotary compressor 100 configured as described above will be described. When the motor unit 20 is driven, a rotational force is transmitted to the main shaft 11. The rotational force transmitted to the main shaft 11 is transmitted to the eccentric shaft portion 12 attached to the main shaft 11, and the piston 16 rotates in the compression chamber 30 together with the eccentric shaft portion 12. When the piston 16 rotates in the compression chamber 30, a low-pressure refrigerant is supplied into the compression chamber 30 from the suction port 50. Furthermore, when the piston 16 rotates, the volume of the compression chamber 30 is reduced and the refrigerant is compressed. The compressed refrigerant is discharged from the discharge mechanism 40 formed in the bearing 14 into the sealed container 1. The vane is pressed against the piston 16 by the high-pressure refrigerant discharged into the hermetic container 1, and slides in the vane groove in the radial direction in conjunction with the movement of the piston 16. Plays a role in partitioning high-pressure space. At this time, the discharge mechanism 40 opens and closes the discharge port 45 according to the pressure difference between the discharge pressure in the sealed container 1 and the internal pressure in the compression chamber 30, and discharges the compressed refrigerant. The discharge pressure in the sealed container 1 varies depending on the operating conditions of the refrigeration cycle. For this reason, the opening and closing operation of the discharge mechanism 40 is performed at a relative level such that the valve body 41 is opened when the pressure exceeds the predetermined pressure with respect to the discharge pressure in the sealed container 1.

FIG. 4 is a view showing the operation of the discharge mechanism 40 according to Embodiment 1 of the present invention. The operation of the discharge mechanism 40 will be described with reference to FIG. First, when the internal pressure in the compression chamber 30 is smaller than the pressure in the sealed container 1, the valve body 41 applies a load in the direction of closing the discharge port 45 by the spring force of the spring material 43 and the pressure in the sealed container 1. receive. In the rotary compressor 100 according to the first embodiment, the valve body 41 is installed at an angle of 45 ° or less from the end face with which the compression chamber 30 contacts. For this reason, as shown in FIG. 4A, the end surface on the discharge port 45 side of the valve body 41 closes the discharge port 45 without unevenness from the end surface of the compression chamber 30 and receives the internal pressure of the compression chamber 30. Become.

Next, the refrigerant is compressed in the compression chamber 30, and the end face on the discharge port 45 side of the valve body 41 receives the internal pressure. When the load due to the internal pressure becomes larger than the resultant pressure of the pressure in the hermetic container 1 and the spring force of the spring member 43, as shown in FIG. The valve body 41 moved moves toward the spring member 43 along the guide hole 42 opened from the side surface of the discharge port 45 and starts to open the discharge port 45. 4C, the end surface of the valve body 41 on the discharge port 45 side receives the fluid force of the discharged refrigerant and opens the valve body 41 greatly. When the discharge of the refrigerant is completed, the valve body 41 moves to the discharge port 45 side by the spring force of the spring material 43 and starts closing the discharge port 45. And the internal pressure of the compression chamber 30 becomes smaller than the pressure in the airtight container 1, and as shown to Fig.4 (a), the front-end | tip by the side of the discharge outlet 45 side by the pressure difference in the airtight container 1 and the compression chamber 30 is shown. Pressed against the end of the guide hole 42, the discharge port 45 is completely closed.

In FIG. 4, the end of the guide hole 42 on the side of the compression chamber 30 is positioned so as to coincide with the end surface 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. Yes, but not necessarily. For example, the position of the end of the guide hole 42 on the compression chamber 30 side may be a position that is outside the inner wall of the cylinder 13, and in that case, a part of the valve body 41 is in contact with the cylinder 13 and close to it. It may be in contact with an elastic body installed on the cylinder 13 or the like. Further, in order to ensure the clearance between the valve body 41 and the piston 16, the end of the guide hole 42 on the side of the compression chamber 30 is positioned slightly closer to the inside of the sealed container 1 than the end surface of the compression chamber 30. Good. Alternatively, the opening on the compression chamber 30 side of the guide hole 42 may be an opening connected to the inside of the sealed container 1 by shortening the length of the discharge port 45 or the like. Further, when the discharge port 45 is greatly opened, the tip of the valve body 41 does not enter the inside of the opening on the side surface of the discharge port 45, and slightly protrudes into the discharge port 45 so that the valve body 41 is partially The discharge port 45 may be covered.

In the rotary compressor 100 of the first embodiment, the discharge path is configured in the order of the compression chamber 30, the valve body 41, and the discharge port 45. The dead volume can be reduced by closing the discharge port 45 with the valve body 41 immediately after the compression chamber 30. For this reason, the efficiency fall of the rotary compressor 100 by re-expansion of a refrigerant | coolant can be suppressed. Here, in the valve body 41, when the valve body 41 closes the discharge port 45, the end surface on the discharge port 45 side of the valve body 41 is not uneven with respect to the end surface on the compression chamber 30 side of the discharge port 45. Installed. For this reason, the end surface of the compression chamber 30 and the end surface of the valve body 41 on the discharge port 45 side coincide with each other on the same plane. That is, the valve body 41 closes the opening surface of the discharge port 45 on the compression chamber 30 side from the inside of the discharge port 45. As a result, the dead volume can be minimized, and the valve body 41 can be prevented from projecting into the compression chamber 30 and colliding with the piston 16. Here, “match” means that the surface of the valve body 41 is a slight distance from the end of the discharge port 45 to ensure clearance, for example, the end surface of the valve body 41 on the discharge port 45 side and the end surface of the compression chamber 30. This distance includes a case where the distance is about 1/10 of the entire length of the discharge port 45. Moreover, in order to increase the area which receives the pressure from the compression chamber 30, in the valve body 41, a recess, a groove, or the like may be formed on the discharge port 45 side of the valve body 41.

FIG. 5 is a diagram showing the ratio of the opening of the discharge port 45 and the ratio of the fluid force acting on the valve element 41 with respect to the installation angle of the valve element 41 according to Embodiment 1 of the present invention. From FIG. 5, the installation angle of the valve body 41 is the same as the angle α at which the guide hole 42 is provided. As the installation angle of the valve body 41 increases, the ratio of the opening of the discharge port 45 to the amount of movement of the valve body 41 decreases. This indicates that when the installation angle of the valve body 41 is increased, the opening width of the discharge port 45 is decreased and the discharge pressure loss is increased. On the other hand, the fluid force acting on the valve body 41 tends to increase as the installation angle increases. For this reason, it becomes easy to open the valve body 41, and an overcompression loss is reduced. Both losses are in a trade-off relationship in the installation angle, but the fluid force can be adjusted by the tip shape of the valve body 41. For this reason, by setting the installation angle to 45 ° or less, it is possible to reduce the dead volume while reducing the discharge pressure loss.

Here, the space in which the guide hole 42 and the spring material 43 are installed may be formed by processing the hollow side surface of the bearing 14 into a hollow shape. Alternatively, the guide hole 42 may be formed by providing a groove on the upper surface of the collar portion and covering the groove with a member having a flat surface that acts as the guide hole 42.

Further, if the communication hole 44 communicates with the space of the spring material 43 and the inside of the sealed container 1 and is immersed in an oil reservoir stored in the bottom of the sealed container 1, the refrigerating machine oil is introduced into the guide hole 42. It is possible to refuel actively. For this reason, the frictional force between the guide hole 42 and the valve body 41 can be reduced. Moreover, the sealing performance of the clearance gap between the guide hole 42 and the valve body 41 improves. For this reason, the refrigerant leakage between the compression chamber 30 and the discharge port 45 can be reduced, and the compressor efficiency can be improved.

The material of the valve body 41 is preferably, for example, a lightweight material with excellent wear resistance and impact resistance, such as a resin material. For this reason, the frictional force at the time of opening and closing can be reduced, the delay in opening and closing of the valve body 41 can be suppressed, and the overcompression loss and the suction overheat loss can be reduced. Furthermore, the impact load with the end portion of the guide hole 42 when the valve body 41 is closed can also be reduced. For this reason, the reliability of the rotary compressor 100 can be improved.

As described above, according to the rotary compressor 100 of the first embodiment, since the valve body 41 opens and closes the discharge port 45 on the opening surface on the compression chamber 30 side, the dead volume can be reduced. it can. For this reason, the re-expansion loss of a refrigerant | coolant can be reduced and compressor efficiency can be improved. Further, the valve body 41 moves from the side surface direction of the discharge port 45 and opens and closes, so that the valve body 41 does not hinder the flow of the refrigerant passing through the discharge port 45. Furthermore, by sliding the valve body 41 through the guide hole 42 of 45 ° or less, the direction in which the refrigerant passing through the discharge port 45 flows and the moving direction of the valve body 41 can be shifted. Thereby, the flow path area can be secured, the discharge pressure loss can be reduced, and the fluid force when the compressed refrigerant is discharged from the compression chamber 30 can be applied in the opening direction of the valve body 41. . For this reason, it becomes easy to open the valve body 41, and an overcompression loss can be reduced.

Embodiment 2. FIG.
FIG. 6 is a diagram illustrating the configuration of the discharge mechanism 40 in the rotary compressor 100 according to Embodiment 2 of the present invention. In the rotary compressor 100 of the second embodiment, the configuration of the devices other than the discharge mechanism 40 is the same as that described in the first embodiment.

In FIG. 6, the discharge mechanism 40 of the second embodiment has a guide groove 46. The guide groove 46 is a groove extending in the radial direction parallel to the end face in contact with the compression chamber 30 and communicating with the discharge port 45. The guide groove 46 is installed so that the valve body 41 reciprocates in the guide groove 46 slidably. Further, the end surface of the valve body 41 on the discharge port 45 side has an inclined portion 47 that is an inclined surface extending from the discharge port 45 to the compression chamber 30 side. The inclined portion 47 is in line contact with the end portion of the guide groove 46. Further, a spring material 43 is installed at the end of the valve body 41 opposite to the discharge port 45 side. A spring force acts in a direction in which the valve body 41 closes the discharge port 45. The space where the spring material 43 is installed and the sealed container 1 communicate with each other through the communication hole 44.

In the discharge mechanism 40 configured as described above, the refrigerant compressed in the compression chamber 30 enters the gap between the inclined portion 47 of the valve body 41 and the end of the guide groove 46, and applies a radial load to the valve body 41. And the valve body 41 is opened. Then, when the compressed refrigerant begins to flow out to the discharge port 45, the fluid force of the refrigerant discharged to the inclined portion 47 is generated, and the valve body 41 is further opened. When the discharge is completed, the valve element 41 is closed by the spring material 43 and pressed against the end of the guide groove 46.

According to the rotary compressor 100 of the second embodiment, the ratio of the opening area of the discharge port 45 to the movement amount of the valve body 41 is larger than that of the rotary compressor 100 of the first embodiment. For this reason, the discharge pressure loss can be further reduced. Further, in the rotary compressor 100 of the first embodiment, the guide groove 46 is formed on the end face of the bearing 14, so that the guide groove 46 can be easily processed. Here, if the angle of the inclined portion 47 is increased, the fluid force of the discharged refrigerant is received, so that the valve body 41 is easily opened. And overcompression of a refrigerant can be prevented. However, when the inclined portion 47 is provided, a gap between the inclined portion 47 and the end portion of the guide groove 46 becomes a dead volume. For this reason, it is necessary to consider the angle of the inclined part 47 as a design item of a compressor.

Embodiment 3 FIG.
FIG. 7 is a diagram illustrating the configuration of the discharge mechanism 40 of the rotary compressor 100 according to Embodiment 3 of the present invention. In the rotary compressor 100 of the third embodiment, the configuration of the devices other than the discharge mechanism 40 is the same as that described in the first and second embodiments.

The rotary compressor 100 of the third embodiment is obtained by changing the shape of the valve body 41 in the discharge mechanism 40 of the second embodiment. As shown in FIG. 7, the valve body 41 has an arc portion 48. The arc portion 48 has a curved end surface on the discharge port 45 side of the valve body 41 and has an arc shape in the direction of the central axis 45a as shown in FIG. The top of the arc in the arc portion 48 is formed so as to coincide with the central portion of the axial thickness of the valve body 41.

In the discharge mechanism 40 configured as described above, the refrigerant compressed in the compression chamber 30 enters the gap between the arc portion 48 of the valve body 41 and the guide groove 46 and generates a radial load on the valve body 41. Then, the valve body 41 is opened. When the compressed refrigerant begins to flow out to the discharge port 45, a fluid force of the refrigerant is generated on the side of the arc portion 48 on the compression chamber 30, and the valve body 41 is further opened. When the discharge is completed, the valve element 41 is closed by the spring material 43 and pressed against the end of the guide groove 46.

According to the rotary compressor 100 of the third embodiment, when the valve body 41 opens the discharge port 45, the end on the discharge port 45 side receives a collision load. For this reason, according to the rotary compressor 100 of the third embodiment, the end on the discharge port 45 side is the arc portion 48, the arc shape is a curved surface as the collision surface, and the top of the arc is the valve element 41. I tried to be in the center. Therefore, the direction of the load in the valve body 41 can be matched with the moving direction of the valve body 41, and the valve body 41 can be prevented from being inclined due to the collision load. For this reason, since the attitude | position of the valve body 41 can be stabilized and the burning of the valve body 41 can be prevented, the reliability of the rotary compressor 100 improves.

Embodiment 4 FIG.
FIG. 8 is a diagram illustrating a configuration example of a refrigeration cycle apparatus according to Embodiment 4 of the present invention. Here, FIG. 8 shows an air conditioner as the refrigeration cycle apparatus. The air conditioner of FIG. 8 constitutes a refrigerant circuit in which an outdoor unit (outdoor unit) 101 and an indoor unit (indoor unit) 200 are connected by a gas refrigerant pipe 300 and a liquid refrigerant pipe 400 to circulate the refrigerant. The outdoor unit 101 includes the rotary compressor 100, the four-way valve 102, the outdoor heat exchanger 103, the expansion valve 104, and the outdoor blower 105 described in the first to third embodiments. The indoor unit 200 includes an indoor heat exchanger 201.

The rotary compressor 100 compresses and discharges the sucked refrigerant. Here, although not particularly limited, the operation frequency of the rotary compressor 100 may be arbitrarily changed by, for example, an inverter circuit. The four-way valve 102 is a valve that switches the refrigerant flow between the cooling operation and the heating operation.

The outdoor heat exchanger 103 performs heat exchange between the refrigerant and air (outdoor air). For example, it functions as an evaporator during heating operation, evaporating and evaporating the refrigerant. Moreover, it functions as a condenser during the cooling operation, and condenses and liquefies the refrigerant. The outdoor blower 105 also sends outdoor air to the outdoor heat exchanger 103 to promote heat exchange between the outdoor air and the refrigerant.

An expansion valve 104 such as a throttling device (flow rate control means) serving as a decompression device is for decompressing and expanding the refrigerant. For example, in the case of an electronic expansion valve or the like, the opening degree is adjusted based on an instruction from a control means (not shown). The indoor heat exchanger 201 performs heat exchange between air to be air-conditioned and a refrigerant, for example. During heating operation, it functions as a condenser and condenses and liquefies the refrigerant. Moreover, it functions as an evaporator during cooling operation, evaporating and evaporating the refrigerant. The indoor blower 202 sends air to be air-conditioned to the indoor heat exchanger 201 and promotes heat exchange between the air and the refrigerant.

As described above, according to the refrigeration cycle apparatus of the fourth embodiment, since the rotary compressor 100 described in the first to third embodiments is included as a device, the entire apparatus can be operated efficiently. It can be carried out.

In Embodiments 1 to 4 described above, the rotary compressor 100 is described as compressing the refrigerant, but the present invention is not limited to this. It can be set as the compressor which compresses other fluids, such as air.

In the above-described fourth embodiment, the refrigeration cycle apparatus taking the air conditioner as an example has been described, but it can also be used for a refrigeration apparatus, a hot water supply apparatus, and the like.

DESCRIPTION OF SYMBOLS 1 Airtight container, 10 Compression mechanism part, 11 Main shaft, 12 Eccentric shaft part, 13 Cylinder, 14 Bearing, 15 Partition plate, 16 Piston, 20 Electric motor part, 21 Rotor, 22 Stator, 30 Compression chamber, 40 Discharge mechanism, 41 valve body, 42 guide hole, 43 spring material, 44 communication hole, 45 discharge port, 45a central axis, 46 guide groove, 47 inclined portion, 48 arc portion, 50 suction port, 60 suction muffler, 100 rotary compressor, 101 Outdoor unit, 102 four-way valve, 103 outdoor heat exchanger, 104 expansion valve, 105 outdoor fan, 200 indoor unit, 201 indoor heat exchanger, 202 indoor fan, 300 gas refrigerant pipe, 400 liquid refrigerant pipe.

Claims

A sealed container as an outer shell,
A compression mechanism that is installed in the sealed container and compresses the sucked fluid in a compression chamber;
A discharge port which is a passage when the fluid compressed by the compression mechanism is discharged from the compression chamber into the sealed container;
A valve body that opens and closes the discharge port, and a discharge mechanism that operates the valve body by a pressure difference between an internal pressure of the compression chamber and a pressure in the sealed container,
The discharge mechanism is a position in which the valve body moves in a direction intersecting the central axis of the discharge port, and the valve body closes the compression chamber side opening surface of the discharge port when the valve body closes the discharge port. Hermetic compressor placed in the.
The hermetic compressor according to claim 1, wherein the valve body opens and closes the discharge port from a side surface side of the discharge port.
The discharge mechanism extends in a direction intersecting the central axis of the discharge port and serves as a guide for the movement of the valve body, and one end on the movement direction side of the valve body is a part of the side surface of the discharge port. An open guide hole or guide groove,
An elastic body for applying an elastic force to the valve body in a direction in which the discharge port is closed,
The valve body is configured to apply an internal pressure of the compression chamber in a direction in which the discharge port opens.
When the internal pressure of the compression chamber becomes smaller than the pressure in the sealed container, the end of the valve body is in contact with the side surface of the discharge port facing it, closing the discharge port,
The end of the said valve body leaves | separates from the side surface of the said discharge port facing this, and opens the said discharge port if it becomes larger than the resultant force of the pressure in the said airtight container, and the spring force of the said elastic body. 2. The hermetic compressor according to 2.
The guide hole has a flat wall that forms an angle of 45 ° or less with the opening surface of the discharge port on the compression chamber side, and communicates with the discharge port.
The elastic body gives an elastic force to the valve body at the end of the valve body opposite to the discharge port side,
The space where the elastic body is installed communicates with the inside of the sealed container,
The valve body moves along the direction of the wall of the guide hole, and when the discharge port is closed, the end on the discharge port side and the end of the guide hole are in line contact, and The hermetic compressor according to claim 3, wherein the hermetic compressor has a surface that matches the end surface of the compression chamber without unevenness.
The guide groove has a wall parallel to the end surface of the compression chamber, communicates with the discharge port,
The elastic body is held at the end of the valve body on the side opposite to the discharge port side,
The space where the elastic body is installed communicates with the inside of the sealed container,
The valve body moves in the guide groove along the parallel wall, and when the discharge port is closed, the end on the discharge port side and the end of the guide groove are in line contact. 3. The hermetic compressor according to 3.
6. The hermetic compressor according to claim 5, wherein an end of the valve body on the discharge port side has an inclination extending from the sealed container side to the compression chamber side.
The discharge port side end of the valve body has a curved surface having an arc shape in the moving direction,
The hermetic compressor according to claim 5, wherein an apex of the arc shape is a central portion of a thickness of the valve body in a direction of the central axis of the discharge port.
The hermetic compressor according to any one of claims 1 to 7, comprising a rotary compressor.
A refrigeration cycle apparatus having a refrigerant circuit in which the hermetic compressor, the condenser, the decompression device, and the evaporator according to any one of claims 1 to 8 are connected by piping and the refrigerant is circulated.