Hermetically sealed compressor and refrigeration cycle device

Abstract

A hermetic compressor is provided with: a cylinder in which a compression chamber for compressing a refrigerant and an injection hole constituting a part of an injection flow path for supplying the refrigerant into the compression chamber are formed; closing members which are fixed to both end surfaces of the cylinder in the height direction, respectively, and which close the compression chamber; a discharge valve which is formed on a closing member fixed to one end surface of the cylinder and which opens and closes a discharge port through which the compressed refrigerant is discharged to the outside of the compression chamber; and an injection check valve for opening and closing the injection hole, the discharge valve and the injection check valve being fixed to a different one of a closing member fixed to one end surface of the cylinder and a closing member fixed to the other end surface of the cylinder. When the discharge valve and the injection check valve are projected on the same plane in the height direction of the cylinder, the discharge valve and the injection check valve are disposed at positions at which at least a part of the discharge valve and the injection check valve overlap.

Description

TECHNICAL FIELD

[0001] The present disclosure relates to a hermetic compressor having an injection mechanism and a refrigeration cycle device. BACKGROUND

[0002] A conventional hermetic compressor mounts a motor composed of a rotor and a stator in an upper portion of a hermetic container, and transmits rotation of the motor to a mechanical portion below the motor by a crankshaft fixed to the rotor. The mechanical portion is mainly composed of a cylinder, a main bearing, a sub bearing, an intermediate plate, and a piston. The crankshaft of an eccentric shape rotates, thereby causing the piston to perform eccentric rotation, and the volume of a compression chamber is reduced, thereby compressing a refrigerant.

[0003] In addition, any one or more of the main bearing, the sub bearing, and the intermediate plate is formed with an injection hole in a manner communicating with the compression chamber, and a refrigerant of a liquid or gas at an intermediate pressure is injected from an injection pipe press-fitted or welded to the compression chamber. By increasing the injection refrigerant, the flow rate of the refrigerant discharged from the rotary compressor is increased, and the capacity of the refrigeration cycle is increased. In addition, the injection refrigerant is used to cool the compression mechanism portion, thereby being able to suppress failure of the compressor and improve reliability. In order to reduce deterioration of efficiency of the compressor caused by backflow of the compressed refrigerant to the injection flow path, a check valve is provided in the middle of the injection flow path (for example, refer to Patent Literature 1).

[0004] Patent Literature 1: Japanese Patent Application Publication No. 2019-190302

[0005] The hermetic compressor like that of Patent Literature 1 has the following problem. Since the injection mechanism that injects a refrigerant at an intermediate pressure as an injection refrigerant is provided in the compression chamber, a space in which components of the injection mechanism such as the above-mentioned check valve are arranged is required to be provided in the hermetic container, and this portion causes the hermetic compressor to be large-sized and the manufacturing cost to be increased. SUMMARY

[0006] The present disclosure is made to solve the above-mentioned problem, and aims to provide a hermetic compressor and a refrigeration cycle device that can suppress large-sizing and reduce the manufacturing cost even in the case of having an injection mechanism.

[0007] The hermetic compressor disclosed herein comprises: a cylinder body, which forms a compression chamber for compressing refrigerant, and an injection hole constituting a part of an injection flow path for supplying refrigerant into the compression chamber; a closing component, which is respectively fixed to the two end faces in the height direction of the cylinder body to close the compression chamber; a discharge valve, which is formed in the closing component fixed to one end face of the cylinder body, and opens and closes a discharge port for discharging the compressed refrigerant to the outside of the compression chamber; and an injection check valve, which opens and closes the injection hole, the discharge valve and the injection check valve being fixed to different sides of the closing component fixed to one end face of the cylinder body and the closing component fixed to the other end face of the cylinder body, respectively, and when the discharge valve and the injection check valve are projected onto the same plane in the height direction of the cylinder body, the discharge valve and the injection check valve are arranged in a position where at least part of them overlap.

[0008] Furthermore, the refrigeration cycle device of the present disclosure includes the above-mentioned hermetic compressor.

[0009] According to the disclosed sealed compressor and refrigeration cycle device, the discharge valve and the injection check valve are arranged at positions where they at least partially overlap when projected onto the same plane in the height direction of the cylinder body. Thus, by arranging the injection check valve at the same phase as the discharge valve, the layout of the components of the injection mechanism, etc., is widened, reducing design constraints. This reduces unnecessary space within the sealed container, enabling miniaturization and lowering manufacturing costs. BRIEF DESCRIPTION OF THE DRAWINGS

[0010] Figure 1 It is a schematic diagram showing a longitudinal section of the hermetic compressor according to the embodiment.

[0011] Figure 2 Cut at AA when viewed along the arrow direction Figure 1 A schematic top view of the compression mechanism of a hermetic compressor.

[0012] Figure 3 Cut along the arrow direction at BB Figure 1 A schematic top view of the compression mechanism of a hermetic compressor.

[0013] Figure 4 It is magnified Figure 1 Schematic diagram of the C-arrow portion of a hermetic compressor.

[0014] Figure 5 Cut at DD when viewed in the direction of the arrow Figure 2 A schematic longitudinal section view of the cylinder body with the compression mechanism portion.

[0015] Figure 6It is a schematic diagram showing a longitudinal cross section of a modified example of the hermetic compressor according to the embodiment.

[0016] Figure 7 It is a schematic plan view showing a discharge valve and an injection check valve projected onto an end surface in the height direction of a cylinder of a hermetic compressor according to an embodiment.

[0017] Figure 8 It is a schematic configuration diagram of a refrigeration cycle device including a hermetic compressor according to an embodiment. DETAILED DESCRIPTION

[0018] Hereinafter, embodiments of the present disclosure will be described based on the accompanying drawings. The present disclosure is not limited to the embodiments described below. In the following drawings, the size relationships of the components may differ from the actual size relationships.

[0019] Implementation method.

[0020] Figure 1 It is a schematic diagram showing a longitudinal cross section of the hermetic compressor 100 according to the embodiment. Figure 2 Cut along the arrow direction at AA Figure 1 Schematic top view of the compression mechanism 20 of the hermetic compressor 100. Figure 3 Cut along the arrow direction at BB Figure 1 Schematic top view of the compression mechanism 20 of the hermetic compressor 100. Figure 4 It is magnified Figure 1 Schematic diagram of the C-arrow portion of the hermetic compressor 100. Figure 5 Cut at DD when viewed in the direction of the arrow Figure 2 20 is a schematic longitudinal sectional view of the cylinder 23 of the compression mechanism portion 20. Figure 6 It is a schematic diagram showing a longitudinal cross section of a modified example of the hermetic compressor 100 according to the embodiment.

[0021] The hermetic compressor 100 of the embodiment uses a Figure 1 The single-cylinder rotary compressor of the cylinder 23 shown is a single rotary compressor. Hereinafter, the overall structure of the hermetic compressor 100 as a single rotary compressor will be described.

[0022] like Figure 1As shown, the hermetic compressor 100 includes a compression mechanism 20 for compressing refrigerant gas and a motor 30 for driving the compression mechanism 20 within a hermetic container 10. The hermetic container 10 is composed of an upper container 11 and a lower container 12. The compression mechanism 20 is housed at the bottom of the hermetic container 10, and the motor 30 is housed at the top of the hermetic container 10. The motor 30 is composed of a stator 31 and a rotor 32. The compression mechanism 20 and the motor 30 are connected by a rotating shaft 21 extending in the vertical direction. The rotating shaft 21 transmits the rotational motion of the motor 30 to the compression mechanism 20. In the compression mechanism 20, the refrigerant gas is compressed by the transmitted rotational force and discharged into the hermetic container 10. The hermetic container 10 is filled with compressed high-temperature and high-pressure refrigerant gas, and refrigeration oil is stored at the bottom 10a of the hermetic container 10 to lubricate the compression mechanism 20. An oil pump (not shown) is provided at the lower portion of the rotating shaft 21. The oil pump draws refrigeration oil stored in the bottom 10a of the sealed container 10 while the rotating shaft 21 rotates, and supplies oil to the sliding parts of the compression mechanism 20. Thus, the mechanical lubrication of the compression mechanism 20 is ensured.

[0023] The rotating shaft 21 is composed of a main shaft portion 21a, an eccentric shaft portion 21b, and a secondary shaft portion 21c, which are arranged in this order from top to bottom in the axial direction. The electric motor 30 is shrink-fitted or press-fitted to the main shaft portion 21a, and the cylindrical rotating piston 22 is slidably engaged with the eccentric shaft portion 21b.

[0024] like Figures 1 to 3 As shown, the compression mechanism 20 includes a rotary piston 22, a cylinder 23, an upper bearing 24, a lower bearing 25, and vanes 26. A compression chamber 23a is formed within the cylinder 23. This compression chamber 23a is a cylindrical space open at both ends in the axial direction. The compression chamber 23a houses an eccentric shaft portion 21b of the rotary shaft 21, which moves eccentrically within the compression chamber 23a. The rotary piston 22 is fitted into the eccentric shaft portion 21b. The vanes 26 divide the space formed by the inner circumference of the cylinder 23 and the outer circumference of the rotary piston 22 into a suction side for drawing in refrigerant and a compression side for compressing the refrigerant.

[0025] A blade groove 23c extending radially is formed through the cylinder body 23 in the axial direction. The blade groove 23c is configured so that one radial side opens into the compression chamber 23a and the other radial side forms a back-pressure chamber 23b. The blade groove 23c houses a blade 26. The blade 26 reciprocates radially within the blade groove 23c. The blade 26 is shaped like a roughly rectangular parallelepiped, in which the circumferential thickness of the compression chamber 23a when mounted in the blade groove 23c is less than the radial direction of the compression chamber 23a and the axial length of the compression chamber 23a. A blade spring (not shown) is provided in the back-pressure chamber 23b of the blade groove 23c.

[0026] Normally, high-pressure refrigerant gas within sealed container 10 flows into back-pressure chamber 23b. The pressure differential between the refrigerant gas pressure in back-pressure chamber 23b and the refrigerant gas pressure in compression chamber 23a generates a force that moves vane 26 radially toward the center of compression chamber 23a. This force, generated by the pressure differential between the refrigerant gas pressure in back-pressure chamber 23b and the refrigerant gas pressure in compression chamber 23a, and the radial pressure of the blade spring, causes vane 26 to move radially toward the center of compression chamber 23a. The force that moves vane 26 radially causes one end of vane 26, i.e., the end on the compression chamber 23a side, to come into contact with the cylindrical outer circumference of rotary piston 22. This partitions the space formed by the inner circumference of cylinder 23 and the outer circumference of rotary piston 22. Even when the pressure difference between the refrigerant gas in the sealed container 10, that is, the refrigerant gas in the back-pressure chamber 23b and the refrigerant gas in the compression chamber 23a, is not sufficient to press the vane 26 against the outer periphery of the rotary piston 22, the force of the vane spring can still press one end of the vane 26 against the outer periphery of the rotary piston 22. Therefore, one end of the vane 26 can always abut against the outer periphery of the rotary piston 22.

[0027] like Figure 1 As shown, the upper bearing 24 has a roughly inverted T-shape when viewed from the side, and is engaged with the main shaft portion 21a of the rotating shaft 21 to rotatably support the main shaft portion 21a, and closes the opening portion on one side of the axial direction of the compression chamber 23a. Similarly, the lower bearing 25 has a roughly T-shape when viewed from the side, and is engaged with the secondary shaft portion 21c of the rotating shaft 21 to rotatably support the secondary shaft portion 21c, and closes the opening portion on the other side of the axial direction of the compression chamber 23a. In addition, the upper bearing 24 is provided with a discharge port 24b for discharging the refrigerant gas compressed in the compression chamber 23a to the outside of the compression chamber 23a. As shown Figure 2 As shown, the cylinder 23 is provided with a suction port 23e for sucking low-pressure refrigerant gas from the outside of the closed container 10 into the compression chamber 23a. Figure 2 as well as Figure 5 As shown, a discharge notch 23d is formed in the cylinder 23 to prevent the refrigerant flow path communicating with the discharge port 24b from being rapidly contracted or bent. The discharge notch 23d is formed by cutting out a portion of the inner circumference of the upper end surface of the cylinder 23.

[0028] like Figure 1 As shown, the upper bearing 24 is provided with a strip-shaped discharge valve 24a for closing or opening the discharge port 24b. Figure 7As shown, a fixed portion 24aa is provided on one end of the discharge valve 24a, secured by a fixing member (not shown). A circular head portion 24ab is provided on the other end of the discharge valve 24a, which closes or opens the discharge port 24b. The discharge valve 24a is an on-off valve that rises and falls within the upper bearing 24, acting as a leaf spring. The head portion 24ab closes or opens the discharge port 24b. This controls the timing of the discharge of high-temperature, high-pressure refrigerant gas from the compression chamber 23a through the discharge port 24b. Specifically, the discharge valve 24a closes the discharge port 24b via the head portion 24ab until the refrigerant gas compressed within the compression chamber 23a of the cylinder 23 reaches a predetermined pressure. Once the pressure exceeds the predetermined pressure, the discharge port 24b opens, allowing the high-temperature, high-pressure refrigerant gas to be discharged from the compression chamber 23a. The upper bearing 24 is also referred to as a closing member.

[0029] Here, a rotary compressor having a plurality of cylinders 23 may be used for the hermetic compressor 100 of the embodiment instead of the single rotary compressor described above. Figure 6 In the case of a twin-rotary compressor with cylinders 23 shown in FIG. 1 , the compression mechanism 20 includes, in addition to the aforementioned rotary piston 22, cylinder 23, upper bearing 24, lower bearing 25, and vanes 26, an intermediate plate 28. Similar to the upper bearing 24, the lower bearing 25 is also provided with a discharge port 24b and a discharge valve 24a. In this case, the upper bearing 24 and the lower bearing 25 are also referred to as sealing members. Furthermore, each of the two cylinders 23 is provided with a suction port 23e. That is, each cylinder 23 is provided with one suction port 23e and one discharge port 24b.

[0030] like Figures 2 to 4As shown, a radially extending horizontal injection hole 70 is formed in the cylinder body 23, and an injection pipe connection portion 71 is formed radially outwardly of the injection hole 70, communicating with the injection hole 70. Furthermore, the injection pipe 107 is connected to the injection pipe connection portion 71. Furthermore, a vertical injection hole 72 is formed in the cylinder body 23, extending in the height direction (or axial direction). The vertical injection hole 72 is formed near the radially inner front end of the injection hole 70. Hereinafter, the horizontal injection hole 70 and the vertical injection hole 72 will be collectively referred to as the injection hole. These injection holes constitute part of the injection flow path for the injection refrigerant flowing from the injection pipe 107 into the compression chamber 23a. The end of the horizontal injection hole 70 on the compression chamber 23a side is located farther outward than the inner circumference of the cylinder body 23 and is separated from the compression chamber 23a. Therefore, the horizontal injection hole 70 is not connected to the compression chamber 23a. Furthermore, a conical front end hole 70a is formed at the radially inner front end of the horizontal injection hole 70. In addition, an injection check valve operating groove 77 is formed on the inner circumference of the cylinder body 23 and on one end surface in the height direction of the cylinder body 23. The injection check valve operating groove 77 is open so that the inner circumference of the cylinder body 23 faces the center of the cylinder body 23. Moreover, the injection vertical hole 72 is configured so that one end side in the axial direction is connected to the injection horizontal hole 70, and the other end side is connected to the injection check valve operating groove 77. In other words, the injection vertical hole 72 extends to the end surface in the height direction of the cylinder body 23. Here, the injection vertical hole 72 can also be connected to the front end hole 70a. If the injection vertical hole 72 is not connected to the front end hole 70a, the injection vertical hole 72 must be arranged on the outer circumference of the cylinder body 23, which is restricted by the placement of the injection check valve 74. However, by connecting the injection vertical hole 72 to the front end hole 70a, the injection vertical hole 72 can be arranged on the center side of the cylinder body 23, which can reduce the restrictions on the placement of the injection check valve 74.

[0031] The injection check valve operation groove 77 is provided with an elongated injection check valve 74 and an elongated injection check valve lifting amount control plate 75. Figure 7 As shown, a fixed portion 74a is provided on one end of the injection check valve 74, secured by a fixing member 76, described later. A circular head portion 74b is provided on the other end of the injection check valve 74, which closes or opens the vertical injection hole 72. The injection check valve 74 rises and falls within the injection check valve operating groove 77 and acts as an on-off valve actuated by a leaf spring. The head portion 74b closes or opens the vertical injection hole 72. This controls the timing of the injection refrigerant flowing from the injection pipe 107 through the injection hole into the compression chamber 23a. Furthermore, an injection check valve lift control plate 75 is provided on the opposite side of the injection check valve 74 from the vertical injection hole 72 and is used to limit the lift amount of the injection check valve 74.

[0032] The injection check valve 74 and the injection check valve lift control plate 75 are fixed to one end surface in the height direction of the cylinder 23 by a fixing member 76. The fixing member 76 is, for example, a bolt. Figure 4 As shown, the head portion 76a protrudes outward from the end surface of the cylinder body 23 in the height direction. In a single-rotary compressor, a receiving hole 76b is provided in the lower bearing 25, while in a twin-rotary compressor, a receiving hole 76b for the protruding head portion 76a is provided in the intermediate plate 28. This reduces the depth of the injection check valve operating groove 77, i.e., its axial length, allowing for efficient discharge of compressed refrigerant. Furthermore, the fixing member 76 may be a rivet, for example, rather than a bolt.

[0033] The vertical injection hole 72 is opened and closed by an injection check valve 74, which functions as a leaf spring. Furthermore, an injection check valve lift control plate 75 prevents the injection check valve 74 from excessively rising or falling. Furthermore, an arc-shaped communication portion 73 is formed radially inward of the injection check valve operating groove 77, connecting the vertical injection hole 72 with the compression chamber 23a. Thus, the injection check valve operating groove 77 communicates with the compression chamber 23a via the communication portion 73.

[0034] When the injection refrigerant's pressure in the compression chamber 23a is lower than the injection pressure, it pushes upward on the injection check valve 74, allowing it to flow into the compression chamber 23a. This increases the flow rate of refrigerant compressed and discharged by the cylinder 23 by an amount equivalent to the injection refrigerant. Furthermore, when compression is ongoing and high pressure is present in the compression chamber 23a, the injection check valve 74, located at the height end surface of the cylinder 23, closes the injection vertical hole 72, preventing backflow of high-pressure refrigerant from the compression chamber 23a into the injection vertical hole 72.

[0035] Furthermore, even when there are multiple cylinders 23, one injection mechanism can be provided for each cylinder 23. Specifically, the same number of compression chambers 23a as the number of cylinders 23 is provided, and each compression chamber 23a is provided with an injection mechanism for injecting refrigerant at an intermediate pressure. The components of the injection mechanism in this embodiment are the suction port 23e, the discharge valve 24a, the discharge port 24b, the injection horizontal hole 70, the front end hole 70a, the injection pipe connection portion 71, the injection vertical hole 72, the communication portion 73, the injection check valve 74, the injection check valve lift control plate 75, the fixing member 76, and the injection check valve actuation groove 77.

[0036] Since the suction, compression, and discharge operations are repeated in the compression chamber 23a, the refrigerant gas discharged from the discharge port 24b is discharged intermittently, causing noise such as pulsation. In order to reduce this noise, Figure 1As shown, a discharge muffler 27 is mounted on the outer side of the upper bearing 24, i.e., on the side of the motor 30, so as to cover the upper bearing 24. The discharge muffler 27 is formed with a space formed by the discharge muffler 27 and the upper bearing 24, and a discharge hole (not shown) communicating with the interior of the sealed container 10. The refrigerant gas discharged from the cylinder 23 through the discharge port 24b is temporarily discharged into the space formed by the discharge muffler 27 and the upper bearing 24, and then discharged into the sealed container 10 through the discharge hole.

[0037] like Figure 1 As shown, a suction muffler 101 is provided next to the sealed container 10 for suppressing liquid refrigerant from being directly sucked into the compression chamber 23a of the cylinder 23. Generally speaking, the sealed compressor 100 delivers low-pressure refrigerant gas and liquid refrigerant in a mixed state from the external circuit to which it is connected. When the liquid refrigerant flows into the cylinder 23 and is compressed by the compression mechanism 20, it becomes a cause of failure of the compression mechanism 20. Therefore, in the suction muffler 101, the liquid refrigerant and the refrigerant gas are separated, and only the refrigerant gas is delivered to the compression chamber 23a. The suction muffler 101 is connected to the suction port 23e of the cylinder 23 by a suction connecting pipe 110, and the low-pressure refrigerant gas delivered from the suction muffler 101 is sucked into the compression chamber 23a via the suction connecting pipe 110.

[0038] The compression mechanism 20 is constructed as described above. The eccentric shaft portion 21b of the rotating shaft 21 rotates within the compression chamber 23a of the cylinder 23 due to the rotational motion of the rotating shaft 21. The operating chamber, which is separated by the inner periphery of the compression chamber 23a, the outer periphery of the rotary piston 22 fitted into the eccentric shaft portion 21b, and the vanes 26, increases or decreases in volume as the rotating shaft 21 rotates. First, the operating chamber is connected to the suction port 23e, and low-pressure refrigerant gas is sucked into the operating chamber. Next, the connection between the operating chamber and the suction port 23e is closed, and the refrigerant gas in the operating chamber is compressed while the volume of the operating chamber is reduced. Finally, the operating chamber is connected to the discharge port 24b. After the refrigerant gas in the operating chamber reaches a specified pressure, the discharge valve 24a provided at the discharge port 24b opens, and the refrigerant gas is discharged to the outside of the operating chamber, that is, outside the compression chamber 23a, and discharged as high-temperature and high-pressure refrigerant gas. The high-temperature and high-pressure refrigerant gas discharged from the compression chamber 23a into the sealed container 10 via the discharge muffler 27 passes through the motor 30, rises in the sealed container 10, and is discharged to the outside of the sealed container 10 from the discharge pipe 102 provided at the upper portion of the sealed container 10. A refrigerant circuit for the flow of refrigerant is formed outside the sealed container 10, and the discharged refrigerant circulates in the refrigerant circuit and returns to the suction muffler 101 again.

[0039] As described above, each cylinder 23 is provided with a discharge valve 24a and an injection check valve 74. Figures 1 to 4As shown, the discharge valve 24a sets the blade 26 line-symmetrically at a position approximately opposite to the suction port 23e. In addition, the injection check valve 74 also sets the blade 26 line-symmetrically at a position approximately opposite to the suction port 23e. That is, the discharge valve 24a and the discharge port 24b and the injection check valve 74 and the injection vertical hole 72 are arranged at approximately the same phase. The phase mentioned here refers to the revolution phase of the rotary piston 22. However, the discharge valve 24a and the injection check valve 74 do not contact each other. Here, the discharge valve 24a is arranged on the upper bearing 24 side, and in the case of a single-rotary compressor, the injection check valve 74 is arranged on the lower bearing 25 side, and in the case of a double-rotary compressor, it is arranged on the middle plate 28 side.

[0040] Figure 7 2 is a schematic plan view of the discharge valve 24a and the injection check valve 74 projected onto the end surface in the height direction of the cylinder 23 of the sealed compressor 100 according to the embodiment. Figure 7 As shown, when the discharge valve 24a and the injection check valve 74 are projected onto the same end surface in the height direction of the cylinder body 23, the two on-off valves are positioned so as to interfere with each other. Specifically, when the discharge valve 24a and the injection check valve 74 are projected onto the same plane in the height direction, the two on-off valves are positioned so as to at least partially overlap. By arranging the two on-off valves in the same phase, the layout of the components of the injection mechanism is widened, reducing design constraints. Consequently, unnecessary space within the sealed container 10 can be reduced, enabling miniaturization and, consequently, lowering manufacturing costs.

[0041] In addition, although one discharge valve 24a and one injection check valve 74 are provided in each cylinder 23 in the embodiment, the present invention is not limited thereto, and multiple (two or more) discharge valves 24a and injection check valves 74 may be provided in each cylinder 23. In this case, when the multiple discharge valves 24a and the multiple injection check valves 74 are projected onto the same plane in the height direction, they may be arranged at a position where at least one of the multiple discharge valves 24a overlaps with at least one of the multiple injection check valves 74.

[0042] The hermetic compressor 100 of the embodiment has a displacement of approximately 60cc. Furthermore, in the embodiment, the injection check valve 74 has a longitudinal length of 10mm and a head 74b of 6mm in diameter. The discharge valve 24a has a longitudinal length of 25mm and a head 24ab of 15mm in diameter. Here, the injected refrigerant is compressed and discharged along with the refrigerant from the main circuit flowing in through the suction port 23e. Therefore, the flow rate of the injected refrigerant is always less than the flow rate of the discharged refrigerant, and the size of the injection check valve 74 does not require the size of the discharge valve 24a. Therefore, it is preferable that the longitudinal length of the injection check valve 74 is shorter than the longitudinal length of the discharge valve 24a, and the diameter of the head 74b of the injection check valve 74 is smaller than the diameter of the head 24ab of the discharge valve 24a. By making the injection check valve 74 smaller than the discharge valve 24a, which does not require the size of the discharge valve 24a, unnecessary space within the sealed container 10 can be reduced, thereby achieving miniaturization and reducing manufacturing costs.

[0043] Figure 8 1 is a schematic diagram of a refrigeration cycle device 200 including a hermetic compressor 100 according to an embodiment. Figure 8 A refrigeration cycle device 200 including a hermetic compressor 100 will be described. The refrigeration cycle device 200 is, for example, an air conditioner. The refrigeration cycle device 200 includes: a hermetic compressor 100 having a suction muffler 101 connected to the suction side of the hermetic compressor 100; a flow path switching valve 103 connected to the discharge side of the hermetic compressor 100; an outdoor heat exchanger 104; a pressure reducer 105; and an indoor heat exchanger 106. These are sequentially connected via piping to form a main refrigerant circuit through which refrigerant circulates. Furthermore, the refrigerant circuit includes an injection pipe 107 that branches from a branch point 107c between the pressure reducer 105 and the indoor heat exchanger 106 in the main circuit and is connected to the compression mechanism 20 of the hermetic compressor 100. Furthermore, an injection pressure reducer 107a for adjusting the injection pressure and flow rate, and an injection muffler 107b for rectifying the refrigerant flow, are provided midway along the injection pipe 107. The injection pressure reducer 107a may also serve as a device for switching the injection on and off, or an electromagnetic valve may be separately provided in the injection pipe 107 to switch the injection on and off via the electromagnetic valve.

[0044] The flow switching valve 103 is, for example, a four-way valve, which switches between cooling and heating operations by switching the direction of refrigerant flow. Alternatively, a combination of a two-way valve and a three-way valve may be used as the flow switching valve 103 instead of a four-way valve. The pressure reducer 105 reduces the pressure of the refrigerant, causing it to expand. The pressure reducer 105 is, for example, an electronic expansion valve with adjustable throttling opening. By adjusting the opening, it controls the refrigerant pressure flowing into the indoor heat exchanger 106 during cooling operation and controls the refrigerant pressure flowing into the outdoor heat exchanger 104 during heating operation. The outdoor heat exchanger 104 functions as an evaporator or a condenser, exchanging heat between the air and the refrigerant, causing the refrigerant to evaporate and gasify or condense and liquefy. The outdoor heat exchanger 104 functions as an evaporator during heating operation and as a condenser during cooling operation. The indoor heat exchanger 106 functions as an evaporator or a condenser, exchanging heat between the air and the refrigerant to evaporate or condense the refrigerant. The indoor heat exchanger 106 functions as a condenser during heating operation and as an evaporator during cooling operation.

[0045] In the case of heating operation, the flow path switching valve 103 and Figure 8 The high-temperature and high-pressure refrigerant compressed by the sealed compressor 100 flows to the indoor heat exchanger 106, condenses and liquefies, is throttled by the pressure reducer 105, becomes a low-temperature and low-pressure two-phase state, flows to the outdoor heat exchanger 104, evaporates and gasifies, and returns to the sealed compressor 100 again through the flow path switching valve 103. That is, the refrigerant is Figure 8 Through this cycle, the refrigerant exchanges heat with the outside air in the outdoor heat exchanger 104, which serves as an evaporator. The refrigerant transported to the outdoor heat exchanger 104 absorbs heat and is then transported to the indoor heat exchanger 106, which serves as a condenser, to exchange heat with the indoor air, thereby heating the indoor air.

[0046] In addition, when the heating capacity is further increased during the heating operation, or when the difference between the suction pressure and the discharge pressure is large and the high temperature portion in the compression mechanism 20 is uneven, the valve of the injection pressure reducer 107a is opened to allow the relatively low temperature refrigerant after heat exchange with the indoor air in the indoor heat exchanger 106 to flow into the injection pipe 107 (see Figure 8(bold solid arrow). Since the outlet of the injection pipe 107 is connected to the compression mechanism 20 of the hermetic compressor 100, the relatively low-temperature refrigerant flowing into the injection pipe 107 flows into the compression mechanism 20 of the hermetic compressor 100 as the injection refrigerant. The injection refrigerant flowing into the compression mechanism 20 is then compressed together with the low-pressure refrigerant flowing from the main circuit into the suction muffler 101, and is discharged from the hermetic compressor 100 as a high-temperature, high-pressure refrigerant gas.

[0047] In the case of cooling operation, the flow path switching valve 103 and Figure 8 The high-temperature and high-pressure refrigerant compressed by the sealed compressor 100 flows to the outdoor heat exchanger 104, and after being condensed and liquefied, it is throttled by the pressure reducer 105, becoming a low-temperature and low-pressure two-phase state, and flows to the indoor heat exchanger 106, evaporates and gasifies, and returns to the sealed compressor 100 again through the flow path switching valve 103. That is, when the operation is changed from heating to cooling, the indoor heat exchanger 106 changes from a condenser to an evaporator, and the outdoor heat exchanger 104 changes from an evaporator to a condenser. Therefore, the refrigerant is Figure 8 Through this cycle, the refrigerant exchanges heat with the indoor air in the indoor heat exchanger 106, which serves as an evaporator, absorbing heat from the indoor air, that is, cooling the indoor air. The refrigerant that has absorbed heat is then transported to the outdoor heat exchanger 104, which serves as a condenser, to exchange heat with the outside air and dissipate heat to the outside air.

[0048] The sealed compressor 100 of the embodiment described above includes: a cylinder 23 having a compression chamber 23a for compressing refrigerant and an injection hole forming part of an injection flow path for supplying refrigerant into the compression chamber 23a; a closing member fixed to both end surfaces of the cylinder 23 in the height direction, respectively, to close the compression chamber 23a; a discharge valve 24a formed in the closing member fixed to one end surface of the cylinder 23, to open and close a discharge port 24b for discharging the compressed refrigerant to the outside of the compression chamber 23a; and an injection check valve 74, which opens and closes the injection hole. The discharge valve 24a and the injection check valve 74 are respectively fixed to different sides of the closing member fixed to one end surface of the cylinder 23 and the closing member fixed to the other end surface of the cylinder 23. When the discharge valve 24a and the injection check valve 74 are projected onto the same plane in the height direction of the cylinder 23, the discharge valve 24a and the injection check valve 74 are arranged at a position where they at least partially overlap.

[0049] According to the hermetic compressor 100 of the embodiment, when the discharge valve 24a and the injection check valve 74 are projected onto the same plane in the height direction of the cylinder body 23, the discharge valve 24a and the injection check valve 74 are arranged at a position where they at least partially overlap. Thus, by arranging the injection check valve 74 at the same phase as the discharge valve 24a, the layout of the components of the injection mechanism, etc., is widened, and design constraints are reduced. Consequently, unnecessary space within the hermetic container 10 can be reduced, thereby achieving miniaturization and reducing manufacturing costs.

[0050] In addition, in the sealed compressor 100 of the embodiment, the injection hole has: an injection horizontal hole 70, which extends in the radial direction of the cylinder body 23; and an injection vertical hole 72, which extends in the height direction of the cylinder body 23, and a conical front end hole 70a is formed on the radial outside of the injection horizontal hole 70, and the injection vertical hole 72 is connected to the front end hole 70a.

[0051] In the hermetic compressor 100 of the embodiment, the vertical injection hole 72 is connected to the front end hole 70a. If the vertical injection hole 72 and the front end hole 70a are not connected, the vertical injection hole 72 must be located on the outer periphery of the cylinder 23, which would restrict the placement of the injection check valve 74. However, by connecting the vertical injection hole 72 and the front end hole 70a, the vertical injection hole 72 can be located toward the center of the cylinder 23, reducing the restrictions on the placement of the injection check valve 74. As a result, the layout of the components of the injection mechanism is further expanded, further reducing design constraints. Therefore, unnecessary space within the hermetic container 10 can be further reduced, thereby achieving further miniaturization and further reducing manufacturing costs.

[0052] In addition, in the sealed compressor 100 of the embodiment, the injection check valve 74 and the discharge valve 24a have a long strip shape, the length of the injection check valve 74 in the longitudinal direction is shorter than the length of the discharge valve 24a in the longitudinal direction, and the diameter of the head 74b of the injection check valve 74 is smaller than the head 24ab of the discharge valve 24a.

[0053] According to the embodiment of the sealed compressor 100, the unnecessary space in the sealed container 10 can be further reduced by making the size of the injection check valve 74 smaller than the discharge valve 24a by an amount that does not require the size of the discharge valve 24a, thereby further achieving miniaturization, thereby further reducing the manufacturing cost.

[0054] The present application is not limited to the above-mentioned embodiments as they are, but the components can be modified and embodied in the implementation stage without departing from the scope of the present invention. In addition, multiple components disclosed in the above-mentioned embodiments can be appropriately combined.

[0055] Description of Reference Numerals

[0056] 10...Sealed container; 10a...Bottom; 11...Upper container; 12...Lower container; 20...Compression mechanism; 21...Rotating shaft; 21a...Main shaft; 21b...Eccentric shaft; 21c...Secondary shaft; 22...Rotary piston; 23...Cylinder; 23a...Compression chamber; 23b...Back pressure chamber; 23c...Vanilla groove; 23d...Discharge cutout; 23e...Suction port; 24...Upper bearing; 24a...Discharge valve; 24aa...Fixed portion; 24ab...Head; 24b...Discharge port; 25...Lower bearing; 26...Vanilla; 27...Discharge muffler; 28...Intermediate plate; 30...Motor; 31...Stator; 32...Rotor; 70...Injection hole; 70a... Front end hole; 71...Injection piping connection portion; 72...Injection longitudinal hole; 73...Communication portion; 74...Injection check valve; 74a...Fixed portion; 74b...Head portion; 75...Injection check valve lift control plate; 76...Fixed component; 76a...Head portion; 76b...Accommodation hole; 77...Injection check valve actuation groove; 100...Sealed compressor; 101...Suction muffler; 102...Discharge pipe; 103...Flow path switching valve; 104...Outdoor heat exchanger; 105...Pressure reducer; 106...Indoor heat exchanger; 107...Injection piping; 107a...Injection pressure reducer; 107b...Injection muffler; 107c...Branch point; 110...Suction connecting pipe; 200...Refrigeration cycle device.

Claims

1. A hermetic compressor, characterized in that: have: a cylinder having a compression chamber for compressing refrigerant and an injection hole constituting a portion of an injection flow path for supplying refrigerant into the compression chamber; Closing members, which are respectively fixed to both end surfaces of the cylinder in the height direction to close the compression chamber; a discharge valve formed on the sealing member fixed to one end surface of the cylinder and opening and closing a discharge port for discharging the compressed refrigerant to the outside of the compression chamber; as well as an injection check valve, which opens and closes the injection hole, The discharge valve and the injection check valve are fixed to different ones of the sealing member fixed to one end surface of the cylinder and the sealing member fixed to the other end surface of the cylinder. When the discharge valve and the injection check valve are projected onto the same plane in the height direction of the cylinder, the discharge valve and the injection check valve are arranged at positions where they at least partially overlap.

2. The hermetic compressor according to claim 1, characterized in that: The injection hole has: a horizontal injection hole extending in the radial direction of the cylinder body; and A vertical injection hole extending in the height direction of the cylinder body, A conical front end hole is formed on the radially outer side of the injection horizontal hole. The longitudinal injection hole is communicated with the front end hole.

3. The hermetic compressor according to claim 2, characterized in that: The injection check valve and the discharge valve have an elongated shape. The injection check valve has a shorter length in the longitudinal direction than the discharge valve, and a head portion of the injection check valve has a smaller diameter than the head portion of the discharge valve.

4. A refrigeration cycle device, characterized in that: A hermetic compressor according to any one of claims 1 to 3 is provided.

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