Hermetic compressor and refrigeration cycle device

Abstract

Provided is a hermetic compressor including: a cylinder in which are formed a compression chamber that compresses a refrigerant and an injection hole that constitutes a part of an injection flow path for supplying the refrigerant to the inside of the compression chamber; blocking members that are fixed to both end surfaces of the cylinder in the height direction of the cylinder and that block the compression chamber; a discharge valve that is formed in the blocking member fixed to one of the end surfaces of the cylinder and that opens and closes a discharge port for discharging the compressed refrigerant to the outside of the compression chamber; and an injection check valve that opens and closes the injection hole. The discharge valve and the injection check valve are fixed to the blocking member that is fixed to one of the end surfaces of the cylinder and the blocking member that is fixed to the other one of the end surfaces of the cylinder, respectively or vice versa. When the discharge valve and the injection check valve are projected in the same plane in the height direction of the cylinder, the discharge valve and the injection check valve are disposed at positions where at least parts of the valves overlap.

Description

[Technical Field]

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

[0002] A conventional hermetic compressor has a motor consisting of a rotor and a stator mounted at the top of a sealed container, and the rotation of the motor is transmitted to the mechanical part below by a crankshaft fixed to the rotor. The mechanical part is mainly composed of a cylinder, main bearings, sub-bearings, an intermediate plate, and a piston. The rotation of the eccentric crankshaft causes the piston to rotate eccentrically, reducing the volume of the compression chamber and compressing the refrigerant.

[0003] In addition, one or more of the main bearing, sub-bearing, and intermediate plate are formed with injection holes that communicate with the compression chambers, and intermediate-pressure liquid or gas refrigerant is injected into the compression chambers through press-fit or welded injection piping. Adding this injected refrigerant increases the refrigerant flow rate discharged from the rotary compressor, thereby increasing the capacity of the refrigeration cycle. Furthermore, cooling the compression mechanism with the injected refrigerant can prevent compressor failures and improve reliability. To prevent a decrease in compressor efficiency due to the backflow of compressed refrigerant into the injection flow path, some compressors are equipped with a check valve in the injection flow path (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Publication No. 2019-190302 Summary of the Invention [Problem to be solved by the invention]

[0005] A hermetic compressor such as that disclosed in Patent Document 1 has an injection mechanism that injects an intermediate-pressure refrigerant into a compression chamber as an injection refrigerant. Therefore, it is necessary to provide a space within the hermetic container for installing components of the injection mechanism, such as the check valve. This increases the size of the hermetic container, which leads to an increase in manufacturing costs.

[0006] The present disclosure has been made to solve the above-mentioned problems, and aims to provide a hermetic compressor and a refrigeration cycle device that are small in size and have reduced manufacturing costs even when an injection mechanism is included. [Means for solving the problem]

[0007] A hermetic compressor according to the present disclosure includes a cylinder having a compression chamber for compressing a refrigerant and an injection hole that constitutes part of an injection flow path for supplying the refrigerant into the compression chamber, a closing member fixed to both end faces in a height direction of the cylinder and closing the compression chamber, a discharge valve formed in the closing member fixed to one end face of the cylinder and opening and closing a discharge port that discharges the compressed refrigerant to the outside of the compression chamber, and an injection check valve that opens and closes the injection hole, and the discharge valve and the injection check valve are connected to the closing member fixed to one end face of the cylinder and the other end face of the cylinder. of The discharge valve and the injection check valve are fixed to different sides, and 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 positioned so that they at least partially overlap.

[0008] A refrigeration cycle device according to the present disclosure includes the above-described hermetic compressor. [Effects of the Invention]

[0009] In the hermetic compressor and refrigeration cycle apparatus according to the present disclosure, the discharge valve and the injection check valve are arranged in positions where they at least partially overlap when projected onto the same plane in the height direction of the cylinder. By arranging the injection check valve in the same phase as the discharge valve in this way, the layout of the components of the injection mechanism and other components can be expanded, reducing design constraints, and thereby reducing wasted space within the hermetic container, allowing for a smaller size and thereby reducing manufacturing costs. [Brief explanation of the drawings]

[0010] [Figure 1] 1 is a schematic diagram showing a vertical cross section of a hermetic compressor according to an embodiment; [Figure 2] 2 is a schematic plan view of the hermetic compressor of FIG. 1 taken along line AA, showing the compression mechanism as viewed in the direction of the arrows. [Figure 3] 2 is a schematic plan view of the hermetic compressor of FIG. 1 taken along line BB, showing the compression mechanism as viewed in the direction of the arrow. [Figure 4] 2 is an enlarged schematic view of the hermetic compressor of FIG. 1 taken along the arrow C. FIG. [Figure 5] 3 is a schematic vertical cross-sectional view of the compression mechanism section of FIG. 2 taken along the line DD, showing a cylinder viewed in the direction of the arrow. [Figure 6] FIG. 10 is a schematic diagram showing a vertical cross section of a modified example of the hermetic compressor according to the embodiment. [Figure 7] 3 is a schematic plan view of a discharge valve and an injection check valve projected onto an end surface in a height direction of a cylinder of a hermetic compressor according to an embodiment. FIG. [Figure 8] 1 is a schematic configuration diagram of a refrigeration cycle device including a hermetic compressor according to an embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0011] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. Note that the present disclosure is not limited to the embodiments described below. Also, the size relationships of the components in the drawings may differ from those in reality.

[0012] Embodiment FIG. 1 is a schematic diagram showing a vertical cross section of a hermetic compressor 100 according to an embodiment. FIG. 2 is a schematic plan view of the compression mechanism 20 when the hermetic compressor 100 of FIG. 1 is cut along the line AA, as viewed in the direction of the arrow. FIG. 3 is a schematic plan view of the compression mechanism 20 when the hermetic compressor 100 of FIG. 1 is cut along the line BB, as viewed in the direction of the arrow. FIG. 4 is a schematic enlarged view of the hermetic compressor 100 of FIG. 1 as viewed along the line C. FIG. 5 is a schematic vertical cross section of the compression mechanism 20 of FIG. 2 when the compression mechanism 20 is cut along the line DD, as viewed in the direction of the arrow. FIG. 6 is a schematic diagram showing a vertical cross section of a modified example of the hermetic compressor 100 according to an embodiment.

[0013] The hermetic compressor 100 according to the embodiment is a one-cylinder rotary compressor having one cylinder 23, i.e., a single rotary compressor, as shown in Fig. 1. The overall configuration of the hermetic compressor 100, which is a single rotary compressor, will be described below.

[0014] As shown in FIG. 1, a hermetic compressor 100 includes a compression mechanism 20 that compresses refrigerant gas and an electric motor 30 that drives the compression mechanism 20, housed within a hermetic container 10. The hermetic container 10 is composed of an upper container 11 and a lower container 12, with the compression mechanism 20 housed below the hermetic container 10 and the electric motor 30 housed above the hermetic container 10. The electric motor 30 is comprised of a stator 31 and a rotor 32. The compression mechanism 20 and the electric motor 30 are connected by a rotating shaft 21 that extends vertically. The rotating shaft 21 transmits the rotational motion of the electric motor 30 to the compression mechanism 20, and the refrigerant gas is compressed in the compression mechanism 20 by the transmitted rotational force and discharged into the hermetic container 10. The hermetic container 10 is filled with compressed high-temperature, high-pressure refrigerant gas, and refrigeration oil is stored in a bottom portion 10a of the hermetic container 10 to lubricate the compression mechanism 20. An oil pump (not shown) is provided below the rotating shaft 21, and as the rotating shaft 21 rotates, the oil pump draws up refrigeration oil stored in the bottom 10a of the sealed container 10 and supplies the oil to each sliding part of the compression mechanism 20. This ensures mechanical lubrication of the compression mechanism 20.

[0015] Rotating shaft 21 is composed of main shaft portion 21a, eccentric shaft portion 21b, and counter shaft portion 21c, which are formed in this order from top to bottom in the axial direction. Electric motor 30 is fixed to main shaft portion 21a by shrink fitting or press fitting, and cylindrical rolling piston 22 is slidably fitted into eccentric shaft portion 21b.

[0016] 1 to 3, the compression mechanism 20 includes a rolling piston 22, a cylinder 23, an upper bearing 24, a lower bearing 25, and a vane 26. A compression chamber 23a, which is a cylindrical space open at both axial ends, is formed inside the cylinder 23. The compression chamber 23a contains an eccentric shaft portion 21b of the rotary shaft 21 that performs eccentric motion within the compression chamber 23a, a rolling piston 22 fitted into the eccentric shaft portion 21b, and a vane 26 that divides the space formed by the inner periphery of the cylinder 23 and the outer periphery of the rolling piston 22 into a suction side where the refrigerant is sucked in and a compression side where the refrigerant is compressed.

[0017] A radially extending vane groove 23c is formed in the cylinder 23 and penetrates the cylinder 23 in the axial direction. One radial end of the vane groove 23c opens into the compression chamber 23a, and a back pressure chamber 23b is formed on the other radial end. A vane 26 is housed in the vane groove 23c. The vane 26 reciprocates radially within the vane groove 23c. When attached to the vane groove 23c, the vane 26 has a substantially rectangular parallelepiped shape such that the thickness in the circumferential direction of the compression chamber 23a is smaller than the radial and axial lengths of the compression chamber 23a. A vane spring (not shown) is provided in the back pressure chamber 23b of the vane groove 23c.

[0018] Normally, high-pressure refrigerant gas in the sealed container 10 flows into the back pressure chamber 23b, and the pressure difference between the pressure of the refrigerant gas in the back pressure chamber 23b and the pressure of the refrigerant gas in the compression chamber 23a generates a force that moves the vane 26 radially toward the center of the compression chamber 23a. The force resulting from this pressure difference between the pressure of the refrigerant gas in the back pressure chamber 23b and the pressure of the refrigerant gas in the compression chamber 23a, together with the radial pressing force of the vane spring, moves the vane 26 radially toward the center of the compression chamber 23a. The force that moves the vane 26 radially brings one end of the vane 26, i.e., the end on the compression chamber 23a side, into contact with the cylindrical outer periphery of the rolling piston 22. This partitions the space formed by the inner periphery of the cylinder 23 and the outer periphery of the rolling piston 22. Even when the pressure difference between the refrigerant gas in the sealed container 10, i.e., the pressure of the refrigerant gas in the back pressure chamber 23b and the pressure of the refrigerant gas in the compression chamber 23a, is not sufficient to press the vane 26 against the outer periphery of the rolling piston 22, the force of the vane spring can press one end of the vane 26 against the outer periphery of the rolling piston 22. Therefore, one end of the vane 26 can always abut against the outer periphery of the rolling piston 22.

[0019] As shown in FIG. 1, the upper bearing 24 has a substantially inverted T-shape in side view. It is fitted onto the main shaft portion 21a of the rotary shaft 21 to rotatably support the main shaft portion 21a and closes one axial opening of the compression chamber 23a. Similarly, the lower bearing 25 has a substantially T-shape in side view. It is fitted onto the counter shaft portion 21c of the rotary shaft 21 to rotatably support the counter shaft portion 21c and closes the other axial opening of the compression chamber 23a. The upper bearing 24 also has a discharge port 24b that discharges the refrigerant gas compressed in the compression chamber 23a to the outside of the compression chamber 23a. As shown in FIG. 2 and FIG. 5, the cylinder 23 also has a suction port 23e that draws low-pressure refrigerant gas into the compression chamber 23a from outside the sealed container 10. The cylinder 23 also has a discharge notch 23d to prevent the refrigerant flow path communicating with the discharge port 24b from being suddenly constricted or bent. The discharge notch 23d is formed by cutting out a part of the inner circumferential side of the upper end surface of the cylinder 23.

[0020] As shown in FIG. 1, the upper bearing 24 is provided with a long discharge valve 24a that opens or closes the discharge port 24b. As shown in FIG. 7 (described later), one end of the discharge valve 24a is provided with a fixed portion 24aa that is fixed by a fixing member (not shown), and the other end of the discharge valve 24a is provided with a circular head portion 24ab that opens or closes the discharge port 24b. The discharge valve 24a is an on-off valve that lifts within the upper bearing 24 and operates as a leaf spring, and the head portion 24ab opens or closes the discharge port 24b. This controls the discharge timing of the high-temperature, high-pressure refrigerant gas that is discharged from the compression chamber 23a to the outside of the compression chamber 23a through the discharge port 24b. That is, the discharge valve 24a closes the discharge port 24b with the head portion 24ab until the refrigerant gas compressed in the compression chamber 23a of the cylinder 23 reaches a predetermined pressure. When the pressure reaches or exceeds the predetermined pressure, the discharge valve 24a opens the discharge port 24b to discharge the high-temperature, high-pressure refrigerant gas out of the compression chamber 23a. The upper bearing 24 is also referred to as a blocking member.

[0021] Here, the hermetic compressor 100 according to the embodiment may be a rotary compressor having a plurality of cylinders 23 instead of the single rotary compressor described above. In the case of a twin rotary compressor having two cylinders 23 as shown in FIG. 6, the compression mechanism 20 includes an intermediate plate 28 in addition to the rolling piston 22, cylinder 23, upper bearing 24, lower bearing 25, and vane 26 described above, and the lower bearing 25 is also provided with a discharge port 24b and a discharge valve 24a, just like the upper bearing 24. In this case, the upper bearing 24 and the lower bearing 25 are also referred to as blocking 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.

[0022] As shown in FIGS. 2 to 4, a horizontal injection hole 70 extending in the radial direction is formed in the cylinder 23, and an injection pipe connection 71 communicating with the horizontal injection hole 70 is formed radially outward of the horizontal injection hole 70. The injection pipe connection 71 is connected to the injection pipe 107. The vertical injection hole 72 extending in the height direction (or axial direction) is also formed in the cylinder 23, and the vertical injection hole 72 is formed near the radially inner tip of the horizontal injection hole 70. Hereinafter, the horizontal injection hole 70 and the vertical injection hole 72 will be collectively referred to as the injection hole. This injection hole constitutes part of the injection flow path through which the injection refrigerant flows 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 closer to the outer periphery than the inner periphery of the cylinder 23 and is separated from the compression chamber 23a. Therefore, the horizontal injection hole 70 does not communicate with the compression chamber 23a. A conical tip hole 70a is formed at the radially inner tip of the horizontal injection hole 70. An injection check valve operation groove 77 is formed on one end face of the cylinder 23 in the height direction and on the inner circumferential side of the cylinder 23. The injection check valve operation groove 77 opens on the inner circumferential side of the cylinder 23 toward the center of the cylinder 23. One axial end of the vertical injection hole 72 communicates with the horizontal injection hole 70, and the other axial end communicates with the injection check valve operation groove 77. In other words, the vertical injection hole 72 reaches one end face of the cylinder 23 in the height direction. Here, the vertical injection hole 72 may communicate with the tip hole 70a. If the vertical injection hole 72 and the tip hole 70a were not in communication, the vertical injection hole 72 would have to be located on the outer periphery of the cylinder 23, which would impose restrictions on the placement of the injection check valve 74. However, by communicating the vertical injection hole 72 and the tip hole 70a, the vertical injection hole 72 can be located closer to the center of the cylinder 23, which reduces the restrictions on the placement of the injection check valve 74.

[0023] An elongated injection check valve 74 and an elongated injection check valve lift amount control plate 75 are provided in the injection check valve operation groove 77. As shown in FIG. 7 (described later), one end of the injection check valve 74 is provided with a fixed portion 74a that is fixed by a fixing member 76 (described later), and the other end of the injection check valve 74 is provided with a circular head portion 74b that closes or opens the vertical injection hole 72. The injection check valve 74 is an on-off valve that lifts in the injection check valve operation groove 77 and operates as a leaf spring, and the head portion 74b closes or opens the vertical injection hole 72. This controls the injection timing of the injection refrigerant that flows from the injection pipe 107 into the compression chamber 23a via the injection hole. The injection check valve lift amount control plate 75 is provided on the opposite side of the injection check valve 74 from the injection vertical hole 72, and serves to limit the lift amount of the injection check valve 74.

[0024] The injection check valve 74 and the injection check valve lift control plate 75 are fixed to one end surface of the cylinder 23 in the height direction by a fixing member 76. The fixing member 76 is, for example, a bolt, and as shown in FIG. 4, its head 76a protrudes outward from the end surface of the cylinder 23 in the height direction. A housing hole 76b for housing the protruding head 76a is provided in the lower bearing 25 in the case of a single rotary compressor, or in the intermediate plate 28 in the case of a twin rotary compressor. This makes it possible to reduce the depth of the injection check valve operating groove 77, i.e., its axial length, and to effectively discharge the compressed refrigerant. The fixing member 76 may be a member other than a bolt, for example, a rivet.

[0025] The injection vertical hole 72 is opened and closed by an injection check valve 74, which is a leaf spring. The injection check valve 74 is prevented from lifting excessively by an injection check valve lift amount control plate 75. An arc-shaped communication portion 73 that communicates the injection vertical hole 72 with the compression chamber 23a is formed radially inward of the injection check valve operation groove 77. Therefore, the injection check valve operation groove 77 communicates with the compression chamber 23a via the communication portion 73.

[0026] When the pressure inside the compression chamber 23a is lower than the injection pressure, the injected refrigerant pushes up the injection check valve 74 and flows into the compression chamber 23a. This increases the flow rate of the refrigerant compressed and discharged from the cylinder 23 by the amount of the injected refrigerant. Furthermore, when the compression inside the compression chamber 23a progresses and the pressure becomes high, the injection check valve 74 seats on the end face in the height direction of the cylinder 23 and closes the vertical injection hole 72, preventing backflow of the high-pressure refrigerant from the compression chamber 23a to the vertical injection hole 72.

[0027] Note that even when there are multiple cylinders 23, one injection mechanism is provided for each cylinder 23. Specifically, the same number of compression chambers 23a as the number of cylinders 23 are provided, and an injection mechanism that injects intermediate-pressure refrigerant into each compression chamber 23a is provided. Here, the components of the injection mechanism according to this embodiment are suction port 23e, discharge valve 24a, discharge port 24b, injection horizontal hole 70, tip hole 70a, injection piping connection portion 71, injection vertical hole 72, communication portion 73, injection check valve 74, injection check valve lift amount control plate 75, fixing member 76, and injection check valve operation groove 77.

[0028] Because the compression chamber 23a repeatedly performs suction, compression, and discharge operations, the refrigerant gas discharged from the discharge port 24b is discharged intermittently, causing noise such as pulsation. To reduce this, as shown in FIG. 1, a discharge muffler 27 is attached to the outside of the upper bearing 24, i.e., on the motor 30 side, so as to cover the upper bearing 24. The discharge muffler 27 has a discharge hole (not shown) that communicates the space formed by the discharge muffler 27 and the upper bearing 24 with the inside of the sealed container 10. The refrigerant gas discharged from the cylinder 23 through the discharge port 24b is first discharged into the space formed by the discharge muffler 27 and the upper bearing 24, and then discharged from the discharge hole into the sealed container 10.

[0029] As shown in FIG. 1, a suction muffler 101 is provided next to the hermetic container 10 to prevent liquid refrigerant from being directly drawn into the compression chamber 23a of the cylinder 23. Generally, a hermetic compressor 100 receives a mixture of low-pressure refrigerant gas and liquid refrigerant from an external circuit connected to it. If the liquid refrigerant flows into the cylinder 23 and is compressed by the compression mechanism 20, it could cause a malfunction of the compression mechanism 20. Therefore, the suction muffler 101 separates the liquid refrigerant from the refrigerant gas and sends only the refrigerant gas 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 drawn into the compression chamber 23a via the suction connecting pipe 110.

[0030] As described above, the compression mechanism 20 is configured such that the rotation of the rotary shaft 21 rotates the eccentric shaft portion 21b of the rotary shaft 21 within the compression chamber 23a of the cylinder 23. The volume of the working chamber, defined by the inner periphery of the compression chamber 23a, the outer periphery of the rolling piston 22 fitted in the eccentric shaft portion 21b, and the vane 26, increases or decreases as the rotary shaft 21 rotates. First, the working chamber communicates with the suction port 23e, and low-pressure refrigerant gas is drawn into the working chamber. Next, the communication between the working chamber and the suction port 23e is closed, and the volume of the working chamber decreases, compressing the refrigerant gas within the working chamber. Finally, the working chamber communicates with the discharge port 24b. After the refrigerant gas within the working chamber reaches a predetermined pressure, the discharge valve 24a attached to the discharge port 24b opens, and the refrigerant gas is discharged from the working chamber, i.e., the compression chamber 23a, and the high-temperature, high-pressure refrigerant gas is discharged. The high-temperature, high-pressure refrigerant gas discharged from compression chamber 23a into sealed container 10 via discharge muffler 27 passes through motor 30, rises inside sealed container 10, and is discharged to the outside of sealed container 10 from discharge pipe 102 provided at the top of sealed container 10. A refrigerant circuit through which the refrigerant flows is configured outside sealed container 10, and the discharged refrigerant circulates through the refrigerant circuit and returns to suction muffler 101.

[0031] As described above, one discharge valve 24a and one injection check valve 74 are provided for each cylinder 23. As shown in FIGS. 1 to 4, the discharge valve 24a is provided on a position generally opposite the suction port 23e, symmetrical about the vane 26. Similarly, the injection check valve 74 is provided on a position generally opposite the suction port 23e, symmetrical about the vane 26. In other words, the discharge valve 24a and the discharge port 24b are arranged in roughly the same phase as the injection check valve 74 and the vertical injection hole 72. The phase here refers to the orbital phase of the rolling piston 22. However, the discharge valve 24a and the injection check valve 74 are not in contact with each other. The discharge valve 24a is located on the upper bearing 24 side, and the injection check valve 74 is located on the lower bearing 25 side in the case of a single rotary compressor or on the intermediate plate 28 side in the case of a twin rotary compressor.

[0032] FIG. 7 is a schematic plan view of the discharge valve 24a and the injection check valve 74 projected onto an end face in the height direction of the cylinder 23 of the hermetic compressor 100 according to the embodiment. As shown in FIG. 7, when the discharge valve 24a and the injection check valve 74 are projected onto the same end face in the height direction of the cylinder 23, the two on-off valves are positioned so as to interfere with each other. In other words, 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 each other. By arranging the two on-off valves in the same phase in this way, the layout of the components of the injection mechanism and other components can be more freely arranged, reducing design constraints. This reduces wasted space within the hermetic container 10, allowing for a more compact design and lowering manufacturing costs.

[0033] In the embodiment, one discharge valve 24a and one injection check valve 74 are provided for each cylinder 23, but this is not limiting, and a plurality of (two or more) discharge valves 24a and injection check valves 74 may be provided for each cylinder 23. In this case, when the plurality of discharge valves 24a and the plurality of injection check valves 74 are projected onto the same plane in the height direction, it is sufficient that at least one of the plurality of discharge valves 24a and at least one of the plurality of injection check valves 74 are arranged in a position where they overlap.

[0034] The displacement of the hermetic compressor 100 according to this embodiment is approximately 60 cc. In this embodiment, the injection check valve 74 has a longitudinal length of 10 mm, a head portion 74b of the injection check valve 74 having a diameter of 6 mm, a longitudinal length of the discharge valve 24a of 25 mm, and a head portion 24ab of the injection check valve 74 having a diameter of 15 mm. The injected refrigerant is compressed and discharged together with the refrigerant from the main circuit that flows 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. Therefore, the size of the injection check valve 74 does not need to be as large as the discharge valve 24a. Therefore, it is desirable that the longitudinal length of the injection check valve 74 be shorter than the longitudinal length of the discharge valve 24a, and that the diameter of the head portion 74b of the injection check valve 74 be smaller than the diameter of the head portion 24ab of the discharge valve 24a. In this way, by making the size of the injection check valve 74, which is not required to be as large as the discharge valve 24a, smaller than the discharge valve 24a, it is possible to reduce wasted space within the sealed container 10, thereby making it smaller, and thereby reducing manufacturing costs.

[0035] FIG. 8 is a schematic diagram of a refrigeration cycle apparatus 200 including a hermetic compressor 100 according to an embodiment. Next, the refrigeration cycle apparatus 200 including the hermetic compressor 100 will be described with reference to FIG. The refrigeration cycle apparatus 200 is, for example, an air conditioner. The refrigeration cycle apparatus 200 includes the hermetic compressor 100 with an intake muffler 101 connected to the intake 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 components are sequentially connected via piping to form a main circuit of a refrigerant circuit through which a refrigerant circulates. The refrigerant circuit also includes an injection pipe 107 that branches off 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. 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 in the injection pipe 107. The injection pressure reducer 107a may also serve as a device for switching the injection on and off, or a separate solenoid valve may be provided in the injection pipe 107 to switch the injection on and off.

[0036] The flow path switching valve 103 is, for example, a four-way valve that switches the refrigerant flow direction to switch between cooling and heating operation. Note that the flow path switching valve 103 may be a combination of a two-way valve and a three-way valve instead of a four-way valve. The pressure reducer 105 reduces the pressure of the refrigerant to expand it. The pressure reducer 105 is, for example, an electronic expansion valve that can adjust the aperture. By adjusting the aperture, the pressure of the refrigerant flowing into the indoor heat exchanger 106 during cooling operation and the pressure of the refrigerant flowing into the outdoor heat exchanger 104 during heating operation is controlled. The outdoor heat exchanger 104 functions as an evaporator or condenser, exchanging heat between the air and the refrigerant to evaporate and gasify the refrigerant or condensing and liquefying the refrigerant. 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, and exchanges heat between the air and the refrigerant to evaporate and gasify the refrigerant or condense and liquefy the refrigerant. The indoor heat exchanger 106 functions as a condenser during heating operation and as an evaporator during cooling operation.

[0037] In heating operation, the flow path switching valve 103 is connected to the solid line side in Figure 8. The high-temperature, high-pressure refrigerant compressed by the hermetic compressor 100 flows to the indoor heat exchanger 106, condenses, and liquefies, and is then throttled by the pressure reducer 105 to become a two-phase refrigerant with low temperature and low pressure. The refrigerant then flows to the outdoor heat exchanger 104, evaporates, and gasifies before passing through the flow path switching valve 103 and returning to the hermetic compressor 100. That is, the refrigerant circulates as shown by the solid arrows in Figure 8. Through this circulation, the refrigerant exchanges heat with outside air in the outdoor heat exchanger 104, which serves as an evaporator, and the refrigerant sent to the outdoor heat exchanger 104 absorbs heat. The refrigerant that has absorbed heat is then sent to the indoor heat exchanger 106, which serves as a condenser, where it exchanges heat with the indoor air and warms the indoor air.

[0038] Furthermore, when the heating capacity is further increased during heating operation, or when the difference between the suction pressure and the discharge pressure is large and high-temperature portions are unevenly distributed in the compression mechanism 20, 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 the thick solid arrow in FIG. 8). 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 that has flowed into the injection pipe 107 flows into the compression mechanism 20 of the hermetic compressor 100 as injection refrigerant. The injection refrigerant that has flowed into the compression mechanism 20 is compressed together with the low-pressure refrigerant that has flowed from the main circuit into the suction muffler 101, and is discharged from the hermetic compressor 100 as high-temperature, high-pressure refrigerant gas.

[0039] In cooling operation, the flow path switching valve 103 is connected to the dashed line side in Figure 8. The high-temperature, high-pressure refrigerant compressed by the hermetic compressor 100 flows to the outdoor heat exchanger 104, condenses, and liquefies. After being throttled by the pressure reducer 105, the refrigerant becomes a two-phase refrigerant with low temperature and low pressure. The refrigerant then flows to the indoor heat exchanger 106, evaporates, and gasifies. The flow path switching valve 103 then returns to the hermetic compressor 100. That is, when the operation mode changes 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 circulates as shown by the dashed arrows in Figure 8. Through this circulation, the indoor heat exchanger 106, which serves as an evaporator, exchanges heat with the indoor air, absorbing heat from the indoor air and cooling it. The refrigerant that has absorbed heat is sent to the outdoor heat exchanger 104, which serves as a condenser, where it exchanges heat with the outdoor air and releases heat to the outdoor air.

[0040] As described above, the hermetic compressor 100 according to the embodiment includes the cylinder 23 having the compression chamber 23a that compresses the refrigerant and the injection hole that constitutes part of the injection flow path that supplies the refrigerant into the compression chamber 23a, the closing members fixed to both end faces of the cylinder 23 in the height direction and closing the compression chamber 23a, the discharge valve 24a formed in the closing member fixed to one end face of the cylinder 23 and opening and closing the discharge port 24b that discharges the compressed refrigerant to the outside of the compression chamber 23a, and the injection check valve 74 opening and closing the injection hole, and the discharge valve 24a and the injection check valve 74 are fixed to different ones of the closing member fixed to one end face of the cylinder 23 and the closing member fixed to the other end face of the cylinder 23, and 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 in positions where they at least partially overlap.

[0041] According to the hermetic compressor 100 of the embodiment, the discharge valve 24a and the injection check valve 74 are arranged in positions where they at least partially overlap when projected onto the same plane in the height direction of the cylinder 23. By arranging the injection check valve 74 in the same phase as the discharge valve 24a in this way, the layout of the components of the injection mechanism and the like is broadened and design constraints are reduced, so that wasted space within the hermetic container 10 can be reduced, allowing for a more compact design and thereby reducing manufacturing costs.

[0042] In addition, in the hermetic compressor 100 according to the embodiment, the injection hole has a horizontal injection hole 70 extending in the radial direction of the cylinder 23 and a vertical injection hole 72 extending in the height direction of the cylinder 23, and a conical tip hole 70a is formed radially outside the horizontal injection hole 70, and the vertical injection hole 72 and the tip hole 70a are connected to each other.

[0043] According to the hermetic compressor 100 of this embodiment, the vertical injection hole 72 and the tip hole 70a are in communication. If the vertical injection hole 72 and the tip hole 70a were not in communication, the vertical injection hole 72 would have to be located on the outer periphery of the cylinder 23, which would impose restrictions on the placement of the injection check valve 74. However, by making the vertical injection hole 72 and the tip hole 70a in communication, the vertical injection hole 72 can be located closer to the center of the cylinder 23, which reduces the restrictions on the placement of the injection check valve 74. As a result, the layout of the components of the injection mechanism and other components can be more freely arranged, further reducing design restrictions. This further reduces wasted space within the hermetic container 10, enabling further miniaturization and thereby further reducing manufacturing costs.

[0044] Furthermore, in the hermetic compressor 100 according to the embodiment, the injection check valve 74 and the discharge valve 24a are elongated, 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 head 24ab of the discharge valve 24a.

[0045] According to the hermetic compressor 100 of the embodiment, the size of the injection check valve 74, which is not required as much as the discharge valve 24a, can be made smaller than the discharge valve 24a, thereby further reducing wasted space within the hermetic container 10 and enabling further miniaturization, thereby further reducing manufacturing costs.

[0046] The present application is not limited to the above-described embodiments, and the components may be modified and embodied in practice without departing from the spirit of the invention. In addition, multiple components disclosed in the above-described embodiments may be combined as appropriate. [Explanation of symbols]

[0047] 10 sealed container, 10a bottom, 11 upper container, 12 lower container, 20 compression mechanism, 21 rotating shaft, 21a main shaft, 21b eccentric shaft, 21c countershaft, 22 rolling piston, 23 cylinder, 23a compression chamber, 23b back pressure chamber, 23c vane groove, 23d discharge notch, 23e suction port, 24 upper bearing, 24a discharge valve, 24aa fixed portion, 24ab head, 24b discharge port, 25 lower bearing, 26 vane, 27 discharge muffler, 28 intermediate plate, 30 electric motor, 31 stator, 32 rotor, 70 injection horizontal hole, 70a tip hole, 71 injection piping connection portion, 72 injection vertical hole, 73 communication portion, 74 injection check valve, 74a Fixed part, 74b head, 75 injection check valve lift amount control plate, 76 fixing member, 76a head, 76b storage hole, 77 injection check valve operating groove, 100 hermetic 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 cylinder having a compression chamber for compressing a refrigerant and an injection hole that constitutes a part of an injection flow path for supplying the refrigerant into the compression chamber; a closing member fixed to each of both end surfaces of the cylinder in the height direction and closing the compression chamber; a discharge valve formed in the closing member fixed to one end surface of the cylinder, the discharge valve opening and closing a discharge port through which the compressed refrigerant is discharged to the outside of the compression chamber; an injection check valve that opens and closes the injection hole, the discharge valve and the injection check valve are fixed to different ends of the closing member fixed to one end face of the cylinder and the other end face 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 disposed at positions where they at least partially overlap. Hermetic compressor.

2. The injection hole is an injection lateral hole extending in the radial direction of the cylinder; an injection vertical hole extending in the height direction of the cylinder; a conical tip hole is formed on the radially outer side of the injection horizontal hole, The injection vertical hole and the tip hole are in communication with each other. The hermetic compressor according to claim 1 .

3. the injection check valve and the discharge valve have an elongated shape; The length of the injection check valve in the longitudinal direction is shorter than the length of the discharge valve in the longitudinal direction, and the diameter of the head of the injection check valve is smaller than the diameter of the head of the discharge valve. The hermetic compressor according to claim 2.

4. A compressor comprising the hermetic compressor according to any one of claims 1 to 3. Refrigeration cycle equipment.

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