WO2022118385A1

WO2022118385A1 - Compressor and refrigeration cycle device

Info

Publication number: WO2022118385A1
Application number: PCT/JP2020/044807
Authority: WO
Inventors: 亮濱田
Original assignee: 三菱電機株式会社
Priority date: 2020-12-02
Filing date: 2020-12-02
Publication date: 2022-06-09
Also published as: CZ2023185A3; CN116457575A; JPWO2022118385A1; JP7466693B2

Abstract

This compressor comprises: a closed container; a cylinder which is provided in the closed container and has a compression chamber in which a refrigerant is compressed provided on the interior thereof; a bearing which is provided in the closed container and comprises a discharge port for discharging the refrigerant compressed in the compression chamber; and a discharge mechanism which comprises a guide cover that is provided to the bearing had has a cylindrical section with a guide hole configured on the interior thereof, a valve body that is provided in the guide hole, and a connection member that is provided in the guide hole and connects the guide cover and the valve body, and which opens and closes the discharge port via the movement of the valve body in the guide hole, wherein if ar is the inner diameter of the cylindrical section in the direction orthogonal to the movement direction in which the valve body moves along the guide hole, br is the outermost diameter of the valve body in the direction orthogonal to the movement direction in which the valve body moves along the guide hole, and Δc is the clearabce between the inner diameter ar of the cylindrical section and the outermost diameter br of the valve body, then Δc=ar-br and 1/1000≤Δc/br≤1/100.

Description

Compressor and refrigeration cycle equipment

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

Conventionally, there is a compressor in which the valve body is arranged in the discharge port when the discharge port is closed and the valve body is reciprocated by a spring to reduce the dead volume (see, for example, Patent Document 1).

Japanese Unexamined Patent Publication No. 8-39773

However, in the compressor of Patent Document 1, the opening delay and the closing delay of the discharge port due to the valve body may occur depending on the weight of the valve body. When such a delay in opening and closing the discharge port due to the valve body occurs, there is a problem that refrigerant leakage and overcompression of the high-pressure refrigerant occur, resulting in a decrease in the efficiency of the compressor.

The present disclosure has been made in view of the above circumstances, and provides a compressor and a refrigerating cycle apparatus capable of preventing the opening delay and closing delay of the discharge port due to the valve body and improving the compression efficiency. The purpose.

The compressor according to the present disclosure includes a closed container, a cylinder provided in the closed container and having a compression chamber for compressing a refrigerant inside, and a cylinder provided in the closed container and compressed in the compression chamber. A bearing having a discharge port for discharging the discharged refrigerant, a guide lid having a cylindrical portion provided in the bearing and having a guide hole inside, a valve body provided in the guide hole, and the inside of the guide hole. The valve is provided with a connecting member for connecting the guide lid and the valve body, and is provided with a discharge mechanism for opening and closing the discharge port by moving the valve body in the guide hole. The inner diameter of the cylindrical portion in the direction orthogonal to the moving direction in which the body moves along the guide hole is ar, and the outermost part of the valve body in the direction orthogonal to the moving direction in which the valve body moves along the guide hole. Assuming that the diameter is br and the clearance between the inner diameter ar of the cylindrical portion and the outermost diameter br of the valve body is Δc,
Δc = ar-br
1/1000 ≤ Δc / br ≤ 1/100
Is.

According to the present disclosure, since there is a relationship of Δc = ar-br and 1/1000 ≤ Δc / br ≤ 1/100, the space on the connecting member side of the valve body and the space on the discharge port side of the valve body are sealed. It can enhance the sex. As a result, the moving speed of the valve body can be increased by effectively utilizing the differential pressure between the pressure in the space on the connecting member side of the valve body and the pressure in the space on the discharge port side of the valve body. Therefore, it is possible to prevent the opening delay and the closing delay of the discharge port of the compressor, and it is possible to improve the compression efficiency.

It is a schematic block diagram which shows schematic structure of the compressor which concerns on Embodiment 1. FIG. It is a figure which shows the state which the valve body of the discharge mechanism of the compressor which concerns on Embodiment 1 closes a discharge port. It is a figure which shows the state which the valve body of the discharge mechanism of the compressor which concerns on Embodiment 1 opens a discharge port. It is a figure for demonstrating the clearance between the valve body of the compressor and the guide hole which concerns on Embodiment 1. FIG. It is a side view of the T-shaped valve body of the compressor which concerns on Embodiment 1. FIG. It is a top view of the T-shaped valve body of the compressor which concerns on Embodiment 1. FIG. It is a figure which shows the discharge mechanism which removed the T-shaped valve body of the compressor which concerns on Embodiment 1. It is a figure which shows the case where the 1st discharge mechanism and the 2nd discharge mechanism are provided in the compressor which concerns on Embodiment 1. FIG. It is a refrigerant circuit diagram which shows schematic the refrigerant circuit composition of the refrigerating cycle apparatus which concerns on Embodiment 2. FIG. It is a figure which shows the gas density of the refrigerant sucked by a compressor and the gas density of the refrigerant discharged from a compressor for each refrigerant under the compressor rated operation conditions of a typical refrigeration cycle specified in ASHRAE. It is a figure which shows an example of the reed valve of a compressor. It is a figure for demonstrating the lifting distance of the valve body of the compressor used in the refrigerating cycle apparatus of Embodiment 3. FIG.

Hereinafter, the compressor according to the embodiment will be described with reference to the drawings. In the drawings, the same components will be described with the same reference numerals, and duplicate explanations will be given only when necessary. The present disclosure may include any combination of configurable configurations among the configurations described in each of the following embodiments. Further, in the drawings, the relationship between the sizes of the constituent members may differ from the actual one. The form of the component represented in the entire specification is merely an example, and is not limited to the form described in the specification. In particular, the combination of components is not limited to the combination in each embodiment, and the components described in other embodiments can be applied to another embodiment. In addition, the height of pressure and temperature is not determined in relation to the absolute value, but is relatively determined in the state and operation of the device or the like. In the following description, the longitudinal direction of the closed container (vertical direction in the figure) will be described as the axial direction, and the direction passing through the central axis of the closed container and perpendicular to the central axis will be described as the radial direction.

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

The compressor 100 will be described with reference to FIG. The compressor 100 is a component of a refrigerant circuit of a refrigerating cycle device such as a refrigerator, a freezer, a vending machine, an air conditioner, a refrigerating device, or a water heater. Note that FIG. 1 illustrates a rotary compressor as an example of the compressor 100. The compressor 100 can also be applied to a closed type compressor having a discharge valve, such as a scroll compressor and a reciprocating compressor. Further, here, it is assumed that the fluid compressed by the compressor 100 is a refrigerant used in a refrigeration cycle device or the like.

[Compression 100]
The compressor 100 compresses and discharges the sucked refrigerant. The compressor 100 includes a closed container 3. The closed container 3 is composed of a lower container 1 and an upper container 2. The compression mechanism unit 10 and the motor unit 20 are housed in the closed container 3. For example, FIG. 1 shows a state in which the compression mechanism portion 10 is housed in the lower side of the closed container 3 and the motor unit 20 is housed in the upper side of the closed container 3. Further, the bottom of the closed container 3 functions as an oil reservoir in which the refrigerating machine oil is stored. The refrigerating machine oil mainly lubricates the sliding portion of the compression mechanism portion 10.

A first suction pipe 31a and a second suction pipe 31b communicating with the accumulator 300 (see FIG. 9) are connected to the lower container 1 of the closed container 3. 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 also has the same configuration as the first suction pipe 31a and is formed in another cylinder 13. The suction muffler 60 is connected to the accumulator 300 by the low pressure side pipe 155b (see FIG. 9) 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 closed container 3. The compressor 100 takes in a refrigerant (gas refrigerant) from the accumulator 300 into the closed container 3 via the first suction pipe 31a and the second suction pipe 31b. Further, a discharge pipe 2a is connected to the upper part of the upper container 2 of the closed container 3. The compressor 100 discharges the refrigerant compressed by the compression mechanism unit 10 to the outside via the discharge pipe 2a. The accumulator 300 will be described later.
<Compression mechanism 10>
The compression mechanism unit 10 has a function of being driven by the motor unit 20 to compress the refrigerant.

The compression mechanism portion 10 includes a cylinder 13, a rolling piston 16, a bearing 14, a spindle 11, a vane (not shown), and the like.

The cylinder 13 is provided in the closed container 3, has a substantially circular outer circumference, and has a compression chamber 30 inside which is a substantially circular space in a plan view. The cylinder 13 has a predetermined height in the axial direction when viewed from the side. Both ends of the compression chamber 30 in the axial direction are open. Further, the cylinder 13 is provided with a vane groove (not shown) that communicates with the compression chamber 30 and extends in the radial direction so as to penetrate in the axial direction. The compression chamber 30 of the cylinder 13 is a space formed by attaching the bearing 14 and the partition plate 15 to the end portion of the cylindrical cylinder 13 in the spindle 11 direction. In the compression chamber 30, the refrigerant is compressed.

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

Further, the cylinder 13 is provided with a discharge port (not shown) in 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 portion 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 eccentrically rotatable. Further, the rolling piston 16 is slidably fitted to the eccentric shaft portion 12 of the main shaft 11 at the inner peripheral portion.

Vane is stored in the vane groove (not shown). A vane housed in the vane groove is always pressed against the rolling piston 16 by a vane spring (not shown) provided in the back pressure chamber. The compressor 100 has a high pressure inside the closed container 3, and when the operation is started, a force due to the difference pressure between the high pressure inside the closed container 3 and the pressure of the compression chamber 30 acts on the back pressure chamber side on the back side of the vane. .. Therefore, the vane spring is mainly used for the purpose of pressing the vane against the rolling piston 16 at the time of starting the compressor 100 in which there is no difference in pressure between the closed container 3 and the compression chamber 30.

The shape of the vane is a substantially rectangular parallelepiped. Specifically, the vane has a flat substantially rectangular parallelepiped shape in which the length (thickness) in the circumferential direction is smaller than the length in the radial direction and the axial direction.

The bearing 14 is provided in the closed container 3 and is configured in a substantially inverted T shape when viewed from the side surface. The bearing 14 is slidably fitted to the spindle portion 11a, which is a portion above the eccentric shaft portion 12 of the spindle 11. The bearing 14 closes one end face (the end face on the motor portion 20 side) of the compression chamber 30 including the vane groove of 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.

A suction muffler 60 is provided next to the closed container 3. The suction muffler 60 sucks a low-pressure gas refrigerant from the refrigeration cycle. The suction muffler 60 suppresses the liquid refrigerant from being directly sucked into the compression chamber 30 of the cylinder 13 when the liquid refrigerant returns from the refrigeration cycle. The suction muffler 60 is connected to the suction port of the cylinder 13 via the first suction pipe 31a and the second suction pipe 31b. The suction muffler 60 is fixed to the side surface of the closed container 3 by welding or the like.

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

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

The motor unit 20 includes a rotor 21, a stator 22, and the like. The stator 22 abuts on the inner peripheral surface of the closed container 3 and is fixed. The rotor 21 is arranged inside the stator 22 via a gap.

The stator 22 includes at least a stator core in which a plurality of electromagnetic steel sheets are laminated, and a winding wound centrally wound around the teeth of the stator core via an insulating member. Further, a lead wire is connected to the winding of the stator 22. The lead wire is connected to a glass terminal provided in the upper container 2 for supplying electric power from the outside of the closed container 3.

The rotor 21 includes at least a rotor core in which a plurality of electromagnetic steel sheets are laminated and a permanent magnet inserted in the rotor core. The spindle portion 11a of the spindle 11 is shrink-fitted or press-fitted into the center of the rotor core.

<Structure of 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.

A discharge port 45 is formed in the bearing 14. The discharge port 45 is provided at the flange of the bearing 14 so that the compression chamber 30 and the closed 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 into the closed 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 substantially at the same position as the discharge port on the upper surface of the compression chamber 30 formed in the cylinder 13.

As shown in FIGS. 2 and 3, the discharge mechanism 40 has a valve body 41, a spring 43, and a guide lid 46. In FIG. 2, the arrow indicates the high-pressure gas refrigerant applied to the valve body 41 from the compression chamber 30. Further, in FIG. 3, arrows a, b, and c indicate the paths of the high-pressure gas refrigerant.

The guide lid 46 has a cylindrical shape and has a closed 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 closed portion 46a and the inside of the cylindrical portion 46b form a guide hole 42. The closing 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 and the discharge port 45 communicate with each other. The lower end of the cylindrical portion 46b is formed according to the shape of the valve body 41, and the valve body seating portion 46c formed on the bearing 14 is arranged. The valve body seating portion 46c is chamfered. The surface to be chamfered is, for example, 2 [mm] in the height direction and 3 [mm] in the radial direction.

The valve body 41 receives the pressure in the compression chamber 30 and the pressure in the closed container 3 to open and close the discharge port 45. When the pressure in the compression chamber 30 is lower than the pressure in the closed container 3, the valve body 41 is pressed against the discharge port to close the discharge port 45. The valve body 41 is provided 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 hardly causes unevenness with respect to the end face of the discharge port 45 on the compression chamber 30 side. Be placed. Therefore, the end face of the compression chamber 30 and the end face of the valve body 41 on the compression chamber 30 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. Here, "matching" includes the case where the end face of the valve body 41 on the compression chamber 30 side is separated from the end of the discharge port 45 by a slight distance in order to secure clearance or the like. 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 1/10 of the total length of the discharge port 45. Further, in order to increase the area that receives the pressure from the compression chamber 30, in the valve body 41, a dent, a groove, or the like may be 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 closed container 3, the valve body 41 is pushed upward by the pressure in the compression chamber 30 to open the discharge port 45. When the discharge port 45 is opened, the refrigerant compressed in the compression chamber 30 is guided to the outside of the compression chamber 30.

When the discharge port 45 is opened, the high-temperature and high-pressure gas refrigerant discharged from the discharge port 45 is discharged into the closed container 3.

The closed portion 46a and the cylindrical portion 46b of the guide lid 46 are integrally formed, but the closed portion 46a and the cylindrical portion 46b may be formed as separate parts. Further, although the cylindrical portion 46b of the guide lid 46 is formed as a separate body from the bearing 14, it may be formed integrally. The bearing 14, the closed portion 46a and the cylindrical portion 46b are formed of two or three parts. One end of the spring 43, which is a connecting member, is attached to the closing portion 46a of the guide lid 46. One end of the spring 43 is arranged 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 applies 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 closed portion 46a of the guide lid 46 and inside the cylindrical portion 46b of the guide lid 46. Further, the cylindrical portion 46b is provided in a hole provided in the flange portion 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 surface of the compression chamber 30 and the inner wall of the cylinder 13. Further, the lower portion of the bearing 14 coincides with the end surface of the compression chamber 30 and the end surface of the cylinder 13. Further, the space inside the guide lid 46 may be formed by processing from the side surface of the flange portion of the bearing 14. The flat end portion of the guide hole 42 opposite to the compression chamber 30 may be formed by covering it with another part.

The end of the guide hole 42 on the compression chamber 30 side does not necessarily have to coincide with the end surface of the compression chamber 30 provided on the lower side of 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 a position outside the inner wall of the cylinder 13. In this case, a part of the valve body 41 is in contact with the cylinder 13 and is in close contact with or in contact with an elastic body or the like arranged on the cylinder 13. Further, the end of the guide hole 42 on the compression chamber 30 side may be positioned slightly closer to the inside of the closed container 3 than the end surface of the compression chamber 30. As a result, the clearance between the valve body 41 and the rolling piston 16 can be secured.

Further, when the guide lid 46 is a separate part from the bearing 14, the guide lid 46 may be provided inside the flange portion 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 an opening connected to the inner side of the closed container 3. The valve body seating portion 46c may be provided not on the bearing 14 but on the cylindrical portion 46b of the guide lid 46.

A cylindrical communication hole 44 is formed in the closed 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 closed container 3 in which the high-pressure refrigerant discharged from the discharge port 45 is discharged via 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, which is Φ6 mm here. The shape of the communication hole 44 is a circular shape, 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 arranged in the guide hole 42, and when the pressure in the guide hole 42 is larger than the pressure in the compression chamber 30, it slides along the guide hole 42 and moves downward. As a result, the discharge port 45 is closed (see FIG. 2). The side surface of the valve body 41 comes into contact with the side surface of the corresponding discharge port 45 when the valve body 41 closes the discharge port 45. Therefore, the side surface of the discharge port 45 of the valve body 41 is formed so as to have no unevenness with respect to the side surface of the discharge port 45. Further, when the pressure in the guide hole 42 is smaller than the pressure in the compression chamber 30, the valve body 41 moves upward in the guide hole 42. As a result, as shown in FIG. 3, the discharge port 45 is opened.

The density of the material of the valve body 41 is lower than the density of steel. Further, the material of the valve body 41 may be at least a part of a resin material. In the first embodiment, the resin material is PEEK (polyetheretherketone). Further, the resin material may be PAI (polyamideimide) or aluminum.

Furthermore, the surface of the valve body 41 is coated with a metal. In the first embodiment, nickel phosphorus coating is applied. The film thickness of the coating is 10 [μm] to 20 [μm].

When the valve body 41 closes the discharge port 45, the spring 43 is shorter than the natural length.

The inside of the valve body 41 is provided with a fitting portion for fixing the spring 43. The fitting portion fixes the outer diameter or the inner diameter of the end portion of the spring 43.

A rubber material may be provided between the valve body 41 and the valve body seating portion 46c. By providing the rubber material, it is possible to reduce the impact when the valve body 41 is seated on the valve body seating portion 46c and to assist the sealing property. Further, a groove for refueling may be provided in the vicinity of the valve body seating portion 46c. By providing the groove for refueling, it is possible to secure the sealing property by the oil film when the valve body 41 is seated on the valve body seating portion 46c.

The valve body 41 may be in a state in which the tip of the valve body 41 slightly protrudes into the inside of the discharge port 45 and partially covers the discharge port 45 when the discharge port 45 is greatly opened. This makes it possible to prevent the tip of the valve body 41 from entering the inside of the opening on the side surface of the discharge port 45.

FIG. 4 is a diagram for explaining the clearance Δc between the valve body 41 of the compressor 100 and the guide hole 42 according to the first embodiment.

In FIG. 4, the inner diameter of the cylindrical portion 46b in the direction orthogonal to the moving direction in which the valve body 41 moves along the guide hole 42 is defined as ar. Let br be the outermost diameter of the valve body 41 in the direction orthogonal to the moving direction in which the valve body 41 moves along the guide hole 42. The clearance between the inner diameter ar of the cylindrical portion 46b and the outermost diameter br of the valve body 41 is defined as Δc.

In this case, the compressor 100 according to the first embodiment is
Δc = ar-br (1)
1/1000 ≤ Δc / br ≤ 1/100 (2)
Is established.

The coefficient of linear expansion with respect to the temperature of the material of the valve body 41 is different from the coefficient of linear expansion with respect to the temperature of the material of the valve body seating portion 46c. The range of the linear expansion coefficient of the valve body 41 is a range in which the end face of the valve body 41 at the time of sitting does not enter the compression chamber 30 at the maximum discharge temperature of the high-pressure refrigerant in the operating range of the compressor 100.

For example, the height of the valve body 41 is 15 [mm]. The height of the guide hole 42 in which the valve body 41 operates is 30 [mm]. For example, when the outermost diameter br of the valve body 41 is 30 [mm], the clearance Δc is 30 [μm] to 300 [μm].

As shown in FIG. 4, the valve body seating portion 46c of the bearing 14 has a tapered shape. The valve body 41 is seated on the valve body seating portion 46c. The shape of the tip of the valve body 41 on the valve body seating portion 46c side is a chamfered shape and a tapered shape 41_t. The taper angle of the tapered shape 41_t of the valve body 41 coincides with the taper angle of the tapered shape of the valve body seating portion 46c.

The valve body 41 has a hollow portion 41_b inside. The shape of the valve body 41 may have a T-shaped cross section when viewed from a direction orthogonal to the moving direction of the valve body 41.

FIG. 5 is a side view of the T-shaped valve body 41_1 of the compressor 100 according to the first embodiment. FIG. 6 is a top view of the T-shaped valve body 41_1 of the compressor 100 according to the first embodiment. FIG. 7 is a diagram showing a discharge mechanism 40 from which the T-shaped valve body 41_1 of the compressor 100 according to the first embodiment is removed.

As shown in FIGS. 5 to 7, the valve body 41_1 has a T-shaped cross section when viewed from a direction orthogonal to the moving direction of the valve body 41. That is, the cross section of the first portion 41_1_1 orthogonal to the moving direction of the valve body 41_1 is smaller than the cross section orthogonal to the moving direction of the second portion 41_1_1 that opens and closes the discharge port 45.

The first portion 41_1_1 of the valve body 41_1 is attached to the inside of the spring 43. It does not matter how the first portion 41_1_1 of the valve body 41_1 and the spring 43 are attached.

[Operation of compressor 100]
Electric power is supplied to the stator 22 of the motor unit 20 via the lead wire. As a result, a current flows through the winding of the stator 22, and a magnetic flux is generated from the winding. The rotor 21 of the motor unit 20 rotates due to the action of the magnetic flux generated from the winding and the magnetic flux generated from the permanent magnet of the rotor 21. The rotation of the rotor 21 causes the spindle 11 fixed to the rotor 21 to rotate. As the spindle 11 rotates, the rolling piston 16 of the compression mechanism portion 10 eccentrically rotates in 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 vanes (not shown). As the spindle 11 rotates, the volumes of those two spaces change. In one space, the volume gradually expands, and a low-pressure gas refrigerant is sucked from the accumulator 300. In the other space, the volume is gradually reduced, and the gas refrigerant inside is compressed in the compression chamber 30.

The gas refrigerant compressed in the compression chamber 30 and having a high pressure and high 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 closed container 3, and slides radially in the vane groove in conjunction with the movement of the rolling piston 16 to form a compression chamber. It plays a role of partitioning the low pressure space and the high pressure space of 30. 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 closed container 3 and the internal pressure in the compression chamber 30, and discharges the compressed refrigerant. The discharge pressure in the closed container 3 varies depending on the operating conditions of the refrigeration cycle. Therefore, the discharge mechanism 40 opens and closes at a relative height, such as opening the valve body 41 when the pressure exceeds a predetermined pressure with respect to the discharge pressure in the closed container 3. The gas refrigerant discharged from the discharge port 45 is discharged into the space inside the closed container 3 through the discharge port 45 of the discharge muffler 17. The discharged gas refrigerant passes through the gap of the motor unit 20 and is discharged to the outside of the closed container 3 from the discharge pipe 2a connected to the top of the closed container 3. The refrigerant discharged to the outside of the closed container 3 circulates in the refrigeration cycle and returns to the accumulator 300 again.

[Operation of 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 smaller than the internal pressure of the guide hole 42 of the discharge mechanism 40, the valve body 41 tends to close the discharge port 45 by the spring force of the spring 43 and the pressure in the guide hole 42. Receive a load. 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 on the compression chamber 30 side of the valve body 41 receives internal pressure. When the load due to the internal pressure of the end surface of the valve body 41 on the compression chamber 30 side is larger than the resultant force of the internal pressure of the guide hole 42 of the discharge mechanism 40 and the spring force of the spring 43, the discharge port 45 is closed as shown in FIG. The valve body 41 that has been there moves toward the spring 43 side along the guide hole 42. 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 and high-pressure gas refrigerant discharged from the discharge port 45 is discharged into the closed 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 portion of the bearing 14 (arrow a), and passes through the hole provided on the side surface of the guide hole 42 (arrow b). ), Outflow to the inside of the discharge muffler 17. After that, the high-pressure refrigerant inside the discharge muffler 17 passes through the gap formed between the bearing 14 and the discharge muffler 17 and the hole formed in the discharge muffler 17 itself (arrow c), and inside the closed container 3 of the compressor 100. Is discharged to. When the discharge of the refrigerant is completed, the valve body 41 moves toward the discharge port 45 side by the spring force of the spring 43, and starts closing the discharge port 45. Then, the internal pressure of the compression chamber 30 becomes smaller than the pressure inside the closed container 3. Next, as shown in FIG. 2, the tip of the valve body 41 on the compression chamber 30 side is provided at the end of the discharge port 45 by the pressure difference between the pressure in the guide hole 42 and the pressure in the compression chamber 30. It is pressed against the valve seating portion 46c, and the discharge port 45 is completely closed.

The threshold value of the internal pressure of the compression chamber 30 in which the refrigerant discharge operation is performed may be an absolute value. Further, the spring 43 does not need to operate in the guide hole 42, and in order to reduce the pressure loss of the refrigerant passing through the communication hole 44, the spring 43 is provided in a place other than the guide hole 42 to expand the volume of the guide hole 42. Is also good.

Further, the discharge mechanism 40 of the first embodiment does not have to provide the communication hole 44 in the guide lid 46.

Further, the discharge mechanism 40 of the cylinder 13 provided with the second suction pipe 31b may be provided on the bearing 14a on the lower side of the bearing 14.

FIG. 8 is a diagram showing a case where the first discharge mechanism 40_1 and the second discharge mechanism 40_1 are provided in the compressor 100 according to the first embodiment. As shown in FIG. 8, the first discharge mechanism 40_1 is attached to the bearing 14 on the upper side of the cylinder 13, and the second discharge mechanism 40_1 is attached to the bearing 14a on the lower side of the cylinder 13. The configurations of the first discharge mechanism 40_1 and the second discharge mechanism 40_1 are substantially the same as the configurations of the discharge mechanism 40.

The difference between the first discharge mechanism 40_1 and the second discharge mechanism 40_1 is that the mass of the valve body 41 of the second discharge mechanism 40_1 is lighter than the mass of the valve body 41 of the first discharge mechanism 40_1. The spring constant of the spring 43 of the second ejection mechanism 40_1 is larger than the spring constant of the spring 43 of the first ejection mechanism 40_1. The natural length of the spring 43 of the second discharge mechanism 40_1 is shorter than the natural length of the spring 43 of the first discharge mechanism 40_1.

When a plurality of compression chambers 30 and a plurality of discharge mechanisms 40 are provided, the reciprocating operation of the valve body 41 is affected by gravity. To be different. In this case, the mass of the valve body 41 whose operating direction is upward when the discharge port 45 is closed is lighter than the mass of the valve body 41 whose operating direction is downward.

[effect]
According to the compressor 100 of the first embodiment, since there is a relationship of Δc = ar−br and 1/1000 ≦ Δc / br ≦ 1/100, the space on the spring 43 side of the valve body 41 and the valve body 41 It is possible to improve the sealing property with the space on the discharge port 45 side. As a result, the moving speed of the valve body 41 can be increased by effectively utilizing the differential pressure between the pressure in the space on the spring 43 side of the valve body 41 and the pressure in the space on the discharge port 45 side of the valve body 41. .. Therefore, it is possible to provide the compressor 100 that can improve the compression efficiency.

This differential pressure is used not only when the discharge port 45 is closed by the valve body 41, but also when the discharge port 45 is opened when the valve body 41 rises. Therefore, the operation of the valve body 41 can be increased in speed. Further, as compared with the case of using the reed valve, in the compressor 100 of the first embodiment, a large flow path area for discharging the refrigerant is secured, the pressure loss at the time of discharging is reduced, and the compressor efficiency is improved.

Further, since a light resin material is used for the valve body 41, it is possible to reduce the frictional force with the side surface of the cylindrical portion 46b of the valve body 41 when opening and closing the discharge port 45. Therefore, in the compressor 100 of the first embodiment, the opening delay and the closing delay of the valve body 41 can be suppressed, and the overcompression loss and the suction superheat loss can be reduced. Further, the impact load with the end of the guide hole 42 when the valve body 41 closes the discharge port 45 can be reduced. Therefore, the reliability of the compressor 100 can be improved.

Since the valve body 41 is coated with a metal, the reliability of the reciprocating operation of the valve body 41 is improved.

When the valve body 41 closes the discharge port 45, the spring 43 is shorter than the natural length. Therefore, even when the valve body 41 is seated and the refrigerant differential pressure before and after discharge is small, the valve body 41 is seated on the bearing 14 with sufficient sealing property, and the compressor 100 can be operated. Here, the state where the refrigerant differential pressure before and after discharge is small is based on the operating range of a general compressor 100. For example, if the refrigerant is R410A, the discharge side is 2 MPa, the suction side is 1.5 MPa, and the differential pressure is 0. It is a small refrigerant differential pressure of about 5.5 MPa.

According to the compressor 100 of the first embodiment, when the pressure in the guide hole 42 of the guide lid 46 is larger than the pressure in the compression chamber 30, the valve body 41 moves inside the guide hole 42 and is discharged. 45 is closed. The refrigerant discharged from the discharge port 45 is discharged into the closed container 3. Since the communication hole 44 communicates with the space inside the closed container 3, the space inside the guide hole 42 and above the valve body 41 is compressed by the discharged refrigerant having a higher pressure than the refrigerant staying in the guide hole 42. As a result, due to the damper effect, it is possible to suppress the opening delay and the closing delay of the discharge port 45 by the valve body 41.

Further, according to the compressor 100 of the first embodiment, the guide lid 46 is provided with a communication hole 44. 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 closing portion 46a does not completely escape from the communication hole 44, the refrigerant is compressed, and the valve body 41 is pushed back. At this time, the pressure of the refrigerant staying in the space between the valve body 41 and the closing portion 46a is higher than that of the high-pressure refrigerant discharged into the closed container 3 after the compression process is completed. Due to this damper effect, the valve body 41 starts descending immediately after the ascending is completed, and is seated on the valve body seating portion 46c provided in the bearing 14 without delaying closing from the desired seating timing.

Further, according to the compressor 100 of the first embodiment, since the horizontal outer diameter of the communication hole 44 is smaller than the horizontal outer diameter of the valve body 41, the closing speed of the valve body 41 is further increased. It is possible to prevent the decrease.

Further, according to the compressor 100 of the first embodiment, since the end of the guide hole 42 on the compression chamber 30 side is formed so as to coincide with the end surface of the compression chamber 30 and the inner wall of the cylinder 13, the flow of the refrigerant is formed. The road area becomes large and the discharge pressure loss can be reduced.

Further, according to the compressor 100 of the first embodiment, the discharge path is configured to be in the order of the compression chamber 30, the valve body 41, and the discharge port 45. Immediately after the compression chamber 30, the discharge port 45 is closed by the valve body 41. As a result, the dead volume of the compressor 100 can be reduced. Therefore, it is possible to suppress a decrease in efficiency of the compressor 100 due to the re-expansion of the refrigerant.

Further, 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 coincide with each other on the same plane. Therefore, the dead volume of the compressor 100 can be minimized, and the valve body 41 can be prevented from protruding into the compression chamber 30 and colliding with the rolling piston 16.

Further, according to the compressor 100 of the first embodiment, since the cylindrical portion 46b of the guide lid 46 is formed of a separate part from the bearing 14, the structure of the bearing 14 can be simplified and the compression can be performed at low cost. The machine 100 can be provided.

Further, according to the compressor 100 of the first embodiment, when the cylindrical portion 46b of the guide lid 46 is integrally formed with the bearing 14, it is possible to suppress the misalignment between the valve body 41 and the valve body seating portion 46c, so that the reliability is high. The compressor 100 can be provided.

Further, 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. As a result, the communication hole 44 behaves as a throttle portion, and has the effect of not suppressing the damper effect that the communication hole 44 was trying to suppress more than desired. Further, when the discharge port 45 is closed, there is an effect of helping the valve body 41 to close quickly.

Embodiment 2.
FIG. 9 is a refrigerant circuit diagram schematically showing a refrigerant circuit configuration of the refrigerating cycle apparatus 200 according to the second embodiment. The configuration and operation of the refrigeration cycle apparatus 200 will be described with reference to FIG. The refrigerating cycle apparatus 200 according to the second embodiment includes any one of the compressors 100 according to the first embodiment as an element of the refrigerant circuit. Note that FIG. 9 shows a case where the compressor 100 according to the first embodiment is provided for convenience.

<Structure of refrigeration cycle device 200>
The refrigeration cycle device 200 includes a compressor 100, a flow path 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 pipes by the high pressure side pipe 155a and the low pressure side pipe 155b to form a refrigerant circuit. Further, an accumulator 300 is arranged on the upstream side of the compressor 100.

The compressor 100 compresses the sucked refrigerant into 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 the refrigerant between the heating operation and the cooling operation. That is, the flow path switching device 151 is switched so as to connect the compressor 100 and the second heat exchanger 154 during the heating operation, and to connect the compressor 100 and the first heat exchanger 152 during the cooling operation. Can be switched. The flow path switching device 151 may be composed of, for example, a four-way valve. However, a combination of a two-way valve or a three-way valve may be adopted as the flow path switching device 151.

The first heat exchanger 152 functions as an evaporator during the heating operation and as a condenser during the cooling operation. That is, when functioning as an evaporator, the first heat exchanger 152 exchanges heat between the low-temperature low-pressure refrigerant flowing out of the expansion device 153 and, for example, the air supplied by a blower (not shown), and the low-temperature low-pressure liquid. The 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 and high-pressure refrigerant discharged from the compressor 100 and, for example, the air supplied by a blower (not shown), and the high-temperature and high-pressure gas. Refrigerant condenses. The first heat exchanger 152 may be composed of a refrigerant-water heat exchanger. In this case, in the first heat exchanger 152, heat exchange is executed between the refrigerant and a heat medium such as water.

The expansion device 153 expands the refrigerant flowing out from the first heat exchanger 152 or the second heat exchanger 154 to reduce the pressure. The expansion device 153 may be configured by, for example, an electric expansion valve or the like that can adjust the flow rate of the refrigerant. As the expansion device 153, not only an electric expansion valve but also a mechanical expansion valve having a diaphragm for a pressure receiving portion, a capillary tube, or the like can be applied.

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

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

The control device 160 uses information sent from each temperature sensor (not shown) and each pressure sensor (not shown) based on an operation instruction from the user, and uses, for example, a compressor 100, an expansion device 153, and a flow path switching device 151. Etc. to control each actuator.

The control device 160 may be configured by hardware such as a circuit device that realizes the function, or may be configured by an arithmetic unit such as a microcomputer or a CPU and software executed on the arithmetic unit. can.

The control device 160 is composed of dedicated hardware or a CPU (also referred to as a Central Processing Unit, a central processing unit, a processing device, a computing device, a microprocessor, a microprocessor, or a processor) that executes a program stored in a memory. Will be done. When the control device 160 is dedicated hardware, the control device 160 corresponds to, for example, a single circuit, a composite circuit, an ASIC (Application Specific Integrated Circuit), an FPGA (Field Programmable Gate Array), or a combination thereof. do. 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 one 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. Software and firmware are written as programs and stored in memory. The CPU reads and executes a program stored in the memory, and realizes each function of the control device 160. Here, the memory is a non-volatile or volatile semiconductor memory such as RAM, ROM, flash memory, EPROM, EEPROM and the like. It should be noted 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 refrigeration cycle device 200>
Next, the operation of the refrigeration cycle device 200 will be described together with the flow of the refrigerant. Here, the operation of the refrigeration cycle device 200 during the cooling operation will be described by taking as an example the case where the heat exchange fluids in the first heat exchanger 152 and the second heat exchanger 154 are air. In FIG. 9, the flow of the refrigerant during the cooling operation is indicated by a broken line arrow, and the flow of the refrigerant during the heating operation is indicated by a solid line arrow.

By driving the compressor 100, a high-temperature and high-pressure gas-state refrigerant is discharged from the compressor 100. The high-temperature and 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 is performed between the high temperature and high pressure gas refrigerant that has flowed in and the air supplied by the blower (not shown), and the high temperature and high pressure gas refrigerant is condensed and high pressure liquid. It becomes a refrigerant (single phase).

The high-pressure liquid refrigerant sent out from the first heat exchanger 152 becomes a two-phase state refrigerant of a low-pressure gas refrigerant and a liquid refrigerant by the expansion device 153. The two-phase refrigerant flows into the second heat exchanger 154. In the second heat exchanger 154, heat exchange is performed between the flowing two-phase state refrigerant and the air supplied by the blower (not shown), and the liquid refrigerant of the two-phase state refrigerant evaporates. It 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, becomes a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 100 again. Hereinafter, this cycle is repeated.

Therefore, according to the refrigerating cycle device 200 according to the second embodiment, it is possible to provide the refrigerating cycle device 200 using the compressor 100 having good compression efficiency.

The operation of the refrigerating cycle device 200 during the heating operation is executed by making the flow of the refrigerant the flow of the solid line arrow shown in FIG. 9 by the flow path switching device 151.

Note that the flow path of the refrigerant may be set in a fixed direction without providing the flow path switching device 151 provided on the discharge side of the compressor 100.

Further, as an application example of the refrigerating cycle device 200, there are an air conditioner, a water heater, a refrigerator, an air-conditioned hot water supply compound machine, and the like.

Embodiment 3.
In the third embodiment, the types of the refrigerant used in the refrigeration cycle apparatus 200 of the second embodiment will be described.

The refrigerant used in the refrigeration cycle apparatus 200 of the third embodiment is a refrigerant having a lower gas density than the R410A refrigerant. For example, R134a, R1234yf, R513A, R463A, R290, R454C, R454A, R404A, R448A, R449A, R454B, R452B, R466A and the like.

FIG. 10 is a diagram showing the gas density of the refrigerant sucked by the compressor 100 and the gas density of the refrigerant discharged from the compressor 100 for each refrigerant under the compressor rated operating conditions of a typical refrigeration cycle specified in ASHRAE. Is.

Here, ASHRAE is an abbreviation for American Society of Heating, Referraling and Air-Conditioning Engineers (American Society for Thermal Refrigeration and Air Conditioning). The compressor rated operating conditions, also commonly known as ASRAE-T conditions, are a condensation temperature of 54.4 ° C., an evaporation temperature of 7.2 ° C., a supercooling degree of 8.3 ° C., and a superheating degree of 27.8 ° C.

In FIG. 10, the refrigerants of R134a, R1234yf, R513A, R463A, R290, R454C, R454A, R404A, R448A, R449A, R454B, R452B and R466A are shown. As shown in FIG. 10, these refrigerants have a gas density lower than that of R410A, that is, the refrigerant sucked into the compressor 100 and the refrigerant discharged from the compressor 100.

Generally, the pressure loss of a fluid such as a refrigerant gas increases in proportion to the flow velocity of the fluid. When the same refrigerant weight is circulated, the flow velocity of the gas needs to be increased as the density decreases. That is, the low-density refrigerant gas has a larger pressure loss than the high-density refrigerant gas. This pressure loss occurs in various parts of the refrigeration cycle, but its effect is particularly remarkable in places such as compression discharge valves where the flow path is narrow and the fluid flow rate is high.

The pressure loss in the flow path becomes an energy loss, which causes a decrease in the efficiency of the entire refrigeration cycle. A reed valve is generally used for the discharge valve of the rotary compressor 100. FIG. 11 is a diagram showing an example of the reed valve 401 of the compressor 100. As shown in FIG. 11, one end of the lead valve 401 and the regulation plate 402 is fixed by a fixed rivet 403 in the vicinity of the discharge hole 405 provided on the end face of the bearing 14. The regulating plate 402 regulates the movement of the reed valve 401. The lead valve 401 sits on the seating portion 404 and closes the discharge hole 405. The reed valve 401 is lifted by the pressure increase in the compression chamber 30. Since the lead valve 401 has a cantilever structure as described above, the lifting distance R on the fixed portion side of the lead valve 401 from the end face of the bearing 14 is reduced, and the overall flow path area is reduced.

FIG. 12 is a diagram for explaining the lifting distance R of the valve body 41 of the compressor 100 used in the refrigeration cycle device 200 of the third embodiment. As shown in FIG. 12, the valve body 41 of the discharge mechanism 40 of the compressor 100 moves in the guide hole 42 in the vertical direction by the spring 43. Therefore, the lifting distance R becomes uniform in the entire valve body 41, and the flow path area of the entire refrigerant is larger than that of the lead valve 401.

As the flow path area of the refrigerant increases, the flow velocity at the discharge port 45 becomes smaller, and the pressure loss at the discharge port 45 becomes smaller. This effect is remarkable in a refrigerant having a low gas density.

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

The embodiment is presented as an example, and it is possible to intend to limit the scope of claims, and various omissions, replacements, and changes are made without departing from the gist of the embodiment. be able to. These embodiments and variations thereof are included in the scope and gist of the embodiments. Not. The embodiment is carried out in various other forms.

1 lower container, 2 upper container, 2a discharge pipe, 3 closed container, 10 compression mechanism, 11 spindle, 11a spindle, 12 eccentric shaft, 13 cylinder, 14, 14a bearing, 15 partition plate, 16 rolling piston, 17 Discharge muffler, 20 Motor unit, 21 Rotor, 22 Stuff, 30 Compressor chamber, 31a 1st suction pipe, 31b 2nd suction pipe, 40 Discharge mechanism, 40_1 1st discharge mechanism, 40_1 2nd discharge mechanism, 41, 41_1 valve body, 41_1_1 1st part, 41_1_2 2nd part, 41_t tapered shape, 41_b hollow part, 42 guide hole, 43 spring, 44, 44a, 44b, 44c communication hole, 45 discharge port, 46 guide lid, 46a closure part , 46b Cylindrical part, 46c Valve body seating part, 50 suction port, 60 suction muffler, 100 compressor, 141 screw holes, 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 lead valve, 402 regulation plate, 403 fixed rivet, 404 seating part, 405 discharge hole, R lifting distance, ar cylindrical part Inner diameter, outermost diameter of br valve body, Δc clearance.

Claims

With a closed container
A cylinder provided in the closed container and having a compression chamber inside for compressing the refrigerant, and a cylinder.
A bearing provided in the closed container and provided with a discharge port for discharging the refrigerant compressed in the compression chamber, and a bearing.
A guide lid provided on the bearing and having a cylindrical portion having a guide hole inside, a valve body provided in the guide hole, and a valve body provided in the guide hole to connect the guide lid and the valve body. A discharge mechanism for opening and closing the discharge port by moving the valve body in the guide hole is provided.
The inner diameter of the cylindrical portion in the direction orthogonal to the moving direction in which the valve body moves along the guide hole is ar.
Br, the outermost diameter of the valve body in the direction orthogonal to the moving direction in which the valve body moves along the guide hole.
The clearance between the inner diameter ar of the cylindrical portion and the outermost diameter br of the valve body is Δc.
Then
Δc = ar-br
1/1000 ≤ Δc / br ≤ 1/100
The compressor that is.
The compressor according to claim 1, wherein the density of the material of the valve body is lower than the density of steel.
The compressor according to claim 1 or 2, wherein the material of the valve body is at least a part of a resin material.
The compressor according to any one of claims 1 to 3, wherein the surface of the valve body is coated with a metal.
The compressor according to any one of claims 1 to 4, wherein the valve body has a T-shaped cross section when viewed from a side orthogonal to the moving direction of the valve body.
The compressor according to any one of claims 1 to 5, wherein the valve body has a hollow portion inside.
The compressor according to any one of claims 1 to 6, wherein when the valve body closes the discharge port, the connecting member is shorter than the natural length.
The bearing has a tapered valve body seating portion on which the valve body is seated.
The shape of the tip of the valve body on the seating portion side of the valve body has a tapered shape.
The compressor according to any one of claims 1 to 7, wherein the taper angle of the tapered shape of the valve body matches the taper angle of the tapered shape of the valve body seating portion.
The compressor according to claim 8, wherein the coefficient of linear expansion with respect to the temperature of the material of the valve body is different from the coefficient of linear expansion with respect to the temperature of the material of the seating portion of the valve body.
The bearing has an upper bearing and a lower bearing.
The discharge mechanism has a first discharge mechanism provided on the upper bearing and a second discharge mechanism provided on the lower bearing.
The compressor according to any one of claims 1 to 9, wherein the valve body of the second discharge mechanism is lighter than the valve body of the first discharge mechanism.
The connecting member is a spring and
The compressor according to claim 10, wherein the spring constant of the spring of the second ejection mechanism is larger than the spring constant of the spring of the first ejection mechanism.
The compressor according to claim 10 or 11, wherein the natural length of the spring of the second ejection mechanism is shorter than the natural length of the spring of the first ejection mechanism.
A compressor according to any one of claims 1 to 12, a first heat exchanger, an expansion device, and a second heat exchanger are provided.
A refrigeration cycle device in which a refrigerant circulates in the compressor, the first heat exchanger, the expansion device, and the second heat exchanger.
The refrigerating cycle apparatus according to claim 13, wherein the refrigerant is a refrigerant having a gas density lower than that of R410A.
The refrigerating cycle apparatus according to claim 14, wherein the refrigerant is R290.