Compressor and refrigeration cycle device

Abstract

A compressor (1A) comprises: a case (11); a motor (12) accommodated in the case; and a compression mechanism unit (13) accommodated in the case and configured to be capable of being driven by the motor. The inside of the case is under a high-pressure atmosphere filled with a refrigerant after compression by the compression mechanism unit (13). The compression mechanism unit (13) has, around a compression room (Cc), a gas-liquid separation room (Cb) to separate the refrigerant sucked in the compression room into a gas refrigerant and a liquid refrigerant. The gas-liquid separation room (Cb) is at least partially defined by an element forming the compression room (Cc).

Description

[Technical Field]

[0001] An embodiment of the present invention relates to a compressor and a refrigeration cycle device. [Background technology]

[0002] In refrigeration cycle devices used in air conditioners, freezers, etc., an accumulator is installed adjacent to the compressor. The refrigerant circulating through the pipes is introduced into the accumulator before being drawn into the compressor. If the refrigerant contains refrigerant in a liquid or droplet state (called "liquid refrigerant"), this is separated in the accumulator to prevent the liquid refrigerant from being drawn directly into the compressor.

[0003] Refrigeration cycle devices use so-called high-pressure compressors in which a motor and a compression mechanism driven by the motor are housed in a sealed case. Patent Document 1 discloses a high-pressure compressor in which, in addition to a chamber for housing the motor and the compression mechanism, a space used for gas-liquid separation of the refrigerant is provided inside the sealed case. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Utility Model Application Publication No. 04-100077 Summary of the Invention [Problem to be solved by the invention]

[0005] In the compressor of the aforementioned document 1, the interior of the sealed case is divided by a component called an inner shell into a low-pressure section connected to the suction pipe and a high-pressure section connected to the discharge pipe. The low-pressure section is used for gas-liquid separation of the refrigerant, while the motor rotor and compression mechanism are located in the high-pressure section. As a result, the compression chamber is surrounded by a high-pressure atmosphere filled with the discharged refrigerant after compression, and the refrigerant in the low-pressure section is susceptible to heat from the discharged refrigerant. There is still room for improvement in preventing the compression mechanism, particularly the sliding parts of the compression chamber, from overheating. Furthermore, there is a need for further efficiency improvements in the gas-liquid separation of the refrigerant itself.

[0006] Therefore, an object of the present invention is to provide a compressor and a refrigeration cycle device that can suppress overheating of the compression mechanism while realizing more efficient arrangement of the compressor and further promote efficient gas-liquid separation of the refrigerant. [Means for solving the problem]

[0007] A compressor according to an embodiment of the present invention includes a case, a motor housed in the case, and a compression mechanism housed in the case and configured to be drivable by the motor. The inside of the case is a high-pressure atmosphere filled with a refrigerant compressed by the compression mechanism. The compression mechanism has a compression chamber surrounded by: defined at least in part by an element forming the compression chamber; a gas-liquid separation chamber that separates the refrigerant drawn into the compression chamber into a gas refrigerant and a liquid refrigerant; The compressor further has a liquid return passage that opens to a lower portion of the gas-liquid separation chamber when the compressor is installed, communicates with the compression chamber, and is capable of introducing lubricating oil mixed in the gas-liquid separation chamber into the compression chamber. do.

[0008] In this way, by providing the gas-liquid separation chamber around the compression chamber and forming at least a portion of it by the elements that form the compression chamber, the compressor itself has the accumulator function, reducing the space required to install an accumulator separately and enabling a more efficient arrangement of the compressor.

[0009] Furthermore, by providing a gas-liquid separation chamber around the compression chamber, the compression chamber can be cooled by the refrigerant present in the gas-liquid separation chamber, thereby preventing excessive heat from being generated in the sliding parts of the compression mechanism and the refrigerant from becoming overheated after compression.

[0010] The heat generated during the compression of the refrigerant, in other words, the heat transferred from the compression chamber, promotes the evaporation of the liquid refrigerant contained in the refrigerant, thereby reducing the amount of liquid refrigerant itself and making it possible to suppress the intake of liquid refrigerant into the compression chamber, which contributes to efficient gas-liquid separation of the refrigerant.

[0011] The compressor may include a cylindrical cylinder, a rotor rotatably disposed on the inner diameter side of the cylinder, and a vane disposed between the cylinder and the rotor so as to be movable radially relative to the rotor, the vane dividing the space between the cylinder and the rotor into a suction chamber and a compression chamber. In this case, the gas-liquid separation chamber is preferably formed radially outside the compression chamber of the cylinder.

[0012] The compressor can be suitably realized by providing a cylinder and a rotor, and partitioning the suction chamber and compression chamber with vanes. In such a compressor, the gas-liquid separation chamber is formed radially outside the compression chamber, thereby making it possible to reduce the dimensions of the compressor, for example, the height when the compressor is placed vertically.

[0013] The gas-liquid separation chamber is preferably formed on an outer circumferential portion of the cylinder outside the compression chamber in the radial direction.

[0014] In this way, by forming the gas-liquid separation chamber in part of the cylinder, specifically in the outer periphery of the cylinder radially outside the compression chamber, it is possible to reduce the number of parts in the compressor or compression mechanism, reduce the number of joints with other parts, and make it easier to ensure the sealing of the gas-liquid separation chamber.

[0015] It is preferable that the compressor further includes a pair of end plate portions arranged in contact with both axial ends of the cylinder, and each of the end plate portions has an inner diameter portion that closes the space in the cylinder in which the rotor is housed, and an outer diameter portion that closes the gas-liquid separation chamber.

[0016] In this way, by providing an end plate that contacts the axial end of the cylinder and closing the gas-liquid separation chamber with the outer diameter portion of this end plate, there is no need to prepare a separate or dedicated part for closing the gas-liquid separation chamber, which is economical. Furthermore, the inner diameter portion that closes the rotor housing and this outer diameter portion can be finished simultaneously in a single process that includes grinding, etc., which is advantageous in terms of processability.

[0017] The compressor is installed vertically so that the motor is located above the compression mechanism, and further has a liquid return passage that connects the gas-liquid separation chamber with the compression chamber and can introduce lubricating oil mixed in the gas-liquid separation chamber into the compression chamber, and it is preferable that the liquid return passage is formed on a surface of the lower end plate portion that contacts the end face of the cylinder or is defined by the lower end plate portion.

[0018] In this way, in a compressor installed vertically, by forming a liquid return passage that connects the gas-liquid separation chamber and the compression chamber, it is possible to prevent lubricating oil that has entered the compressor along with the refrigerant from accumulating in the gas-liquid separation chamber, thereby preventing a shortage of space that actually contributes to gas-liquid separation of the refrigerant.Furthermore, by forming this liquid return passage on the contact surface with the cylinder of the lower end plate portion or by defining it by the lower end plate portion, it is possible to encourage the flow of lubricating oil into the liquid return passage by gravity.

[0019] The compressor comprises a cylindrical cylinder, a rotor rotatably arranged on the inner diameter side of the cylinder, and a vane arranged between the cylinder and the rotor so as to be movable radially relative to the rotor, dividing the space between the cylinder and the rotor into a suction chamber and a compression chamber, and the gas-liquid separation chamber can also be formed outside the compression chamber in the axial direction of the cylinder.

[0020] The compressor can be suitably realized by providing a cylinder and a rotor, and partitioning the suction chamber and compression chamber with vanes. In such a compressor, the gas-liquid separation chamber is formed outside the compression chamber in the axial direction of the cylinder, thereby making it possible to reduce the dimensions of the compressor, for example, the installation area when the compressor is installed vertically.

[0021] It is preferable that the compressor further includes a bearing arranged outside the compression chamber in the axial direction, the bearing having a bearing portion supporting the rotating shaft of the rotor, and the gas-liquid separation chamber being formed radially outside the bearing portion.

[0022] In this way, in a compressor having a bearing arranged axially outside the compression chamber, the gas-liquid separation chamber is formed radially outside the bearing portion of this bearing, which makes it possible to effectively utilize the space between the motor and the compression mechanism and form the gas-liquid separation chamber while suppressing an increase in the installation area of ​​the compressor.

[0023] The bearing preferably has an inner diameter portion which is the bearing portion and supports the rotating shaft of the rotor, an outer diameter portion which is concentric with the inner diameter portion and spaced radially outward from the inner diameter portion, and a connecting portion which connects the inner diameter portion and the outer diameter portion, and the gas-liquid separation chamber is preferably formed as a space surrounded by the inner diameter portion, the outer diameter portion, and the connecting portion.

[0024] In this way, in addition to the inner diameter portion which is the bearing portion, an outer diameter portion and a connecting portion are provided on the bearing, and the gas-liquid separation chamber is formed as a space surrounded by the inner diameter portion, outer diameter portion and connecting portion, making it easy to ensure the sealing of the gas-liquid separation chamber, particularly the sealing of the compression chamber.

[0025] It is preferable that the bearing further includes a communication passage that connects the gas-liquid separation chamber with the compression chamber and that allows the gas refrigerant present in the gas-liquid separation chamber to be introduced into the compression chamber.

[0026] In this way, a communication passage that connects the gas-liquid separation chamber and the compression chamber is formed in the bearing, and the gas refrigerant present in the gas-liquid separation chamber can be introduced into the compression chamber through this communication passage, so there is no need to prepare special components to form the communication passage, which is economical.

[0027] It is preferable that the compressor further comprises an end plate portion that is arranged in contact with the lower axial end of the cylinder and that closes the space in the cylinder in which the rotor is housed from below, and a pressure bolt that passes through the end plate portion and the cylinder from below in the axial direction, reaches the bearing, and fixes the end plate portion and the cylinder to the bearing by tightening them together.

[0028] In this way, the cylinder and the end plate portion located below it are fastened together by a pressure bolt that passes axially through the cylinder and end plate portion from below and reaches the bearing, thereby preventing the sealing of the gas-liquid separation chamber from being compromised by the use of fasteners, and also making it possible to suppress the effect of liquid refrigerant on the bolt axial force if the liquid refrigerant gets mixed into the gas-liquid separation chamber formed in the bearing.

[0029] A refrigeration cycle device according to another aspect of the present invention includes the compressor, a condenser, an expansion valve, and an evaporator, and the compressor, the condenser, the expansion valve, and the evaporator are connected by refrigerant piping, and the refrigerant discharged from the compressor is circulated to the condenser, the expansion valve, and the evaporator via the refrigerant piping. [Effects of the Invention]

[0030] According to the present invention, it is possible to provide a compressor and a refrigeration cycle device that can suppress overheating of the compression mechanism while realizing more efficient arrangement of the compressor and further promote efficient gas-liquid separation of the refrigerant. [Brief explanation of the drawings]

[0031] [Figure 1] 1 is a schematic diagram showing the overall configuration of a refrigeration cycle device according to an embodiment of the present invention. [Figure 2] FIG. 2 is a cross-sectional view taken along a plane including the central axis of the sealed case, showing the internal configuration of the compressor according to the embodiment. [Figure 3] FIG. 3 is a cross-sectional view taken along line AA shown in FIG. [Figure 4] FIG. 10 is a cross-sectional view taken along a plane including the central axis of the sealed case, showing the internal configuration of a compressor according to another embodiment of the present invention. [Figure 5] 5 is a cross-sectional view showing the internal configuration of the compressor according to the embodiment, taken along a plane that includes the central axis of the sealed case and is different from that of FIG. 4. [Figure 6] 2 is a partial cross-sectional view showing a configuration of a bearing portion of a compression mechanism portion and its surroundings in the compressor according to the embodiment of the present invention; FIG. [Figure 7] 4 is a partial cross-sectional view showing the configuration of a bearing portion of a compression mechanism and its surroundings in a compressor according to a first modified example of the embodiment. FIG. [Figure 8] 10 is a partial cross-sectional view showing the configuration of a bearing portion of a compression mechanism portion and its surroundings in a compressor according to a second modified example of the embodiment. FIG. [Figure 9] FIG. 2 is a partial cross-sectional view showing a support structure for a compression mechanism in the compressor according to the embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0032] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

[0033] FIG. 1 is a schematic diagram showing the overall configuration of a refrigeration cycle apparatus U according to one embodiment of the present invention.

[0034] In this embodiment, the refrigeration cycle apparatus U is a heat pump type refrigeration cycle apparatus. The refrigeration cycle apparatus U can be applied to air conditioners, freezers, refrigerators, hot water heaters, etc., and can also be applied to a heat source unit that cools or heats a fluid to be used that circulates between an external device such as a cooling / heating device or a hot water storage device (not shown). Water is generally used as the fluid to be used, but brine can also be used for purposes such as anti-freezing. The refrigerant circulated through the refrigeration cycle apparatus U is, for example, an HFC refrigerant such as R410A or R32, an HFO refrigerant such as R1234yf, or a natural refrigerant such as carbon dioxide (CO2) or propane.

[0035] The refrigeration cycle apparatus U includes, as its main components, a compressor 1A, a first heat exchanger 2, a second heat exchanger 3, a four-way valve 4, and an expansion valve 5, as well as refrigerant piping 6 that fluidly connects these components and circulates a refrigerant among these components. In the refrigeration cycle apparatus U, the refrigerant circulates while changing phases between a gas refrigerant and a liquid refrigerant.

[0036] The compressor 1A is a so-called high-pressure type compressor, and in this embodiment, is a rotary compressor. As will be described in more detail later, the compressor 1A has a high-pressure-resistant sealed case 11 as its outer shell, and houses a motor 12 and a rotary type compression mechanism 13 driven by the motor 12 inside the case. The compressor 1A may be capable of changing its operating frequency using known inverter control, or may be operated at a constant speed using a commercial frequency.

[0037] The first heat exchanger 2 is installed outdoors and exchanges heat between the outdoor air and the refrigerant. The first heat exchanger 2 is housed in the case of the outdoor unit together with an outdoor fan (not shown) as a component of the outdoor unit. An example of a heat exchanger that can be used as the first heat exchanger 2 is a fin-and-tube type heat exchanger.

[0038] The second heat exchanger 3 is installed indoors and exchanges heat between the refrigerant and the indoor air, which is the fluid to be regulated. The second heat exchanger 3 is housed in the case of the indoor unit together with an indoor blower (not shown) as a component of the indoor unit. As with the first heat exchanger 2, a fin-and-tube type heat exchanger can be used as the second heat exchanger 3.

[0039] The four-way valve 4 switches the flow path of the refrigerant discharged from the compressor 1A between cooling operation (cooling) and heating operation (heating) of the air conditioner. During cooling, the four-way valve 4 sets the refrigerant flow path in a direction from the four-way valve 4 to the first heat exchanger 2. As a result, the refrigerant leaving the four-way valve 4 passes through the first heat exchanger 2 and then flows into the second heat exchanger 3. In contrast, during heating, the refrigerant flow path is switched to a direction from the four-way valve 4 to the second heat exchanger 3. As a result, the refrigerant leaving the four-way valve 4 passes through the second heat exchanger 3 and then flows into the first heat exchanger 2. The first heat exchanger 2 operates as a condenser during cooling and as an evaporator during heating, and the second heat exchanger 3 operates as an evaporator during cooling and as a condenser during heating. In the condenser, the high-temperature, high-pressure gas refrigerant sent from the compressor 1A is changed into high-pressure liquid refrigerant through heat exchange, and in the evaporator, the low-temperature, low-pressure liquid refrigerant sent from the expansion valve 5, which will be described next, is changed into low-pressure gas refrigerant.

[0040] The expansion valve 5 adjusts the pressure of the refrigerant leaving the condenser (specifically, the first or second heat exchanger 2, 3 operating as a condenser) by the action of an orifice, and adjusts the pressure of the refrigerant heading toward the evaporator (specifically, the second or first heat exchanger 3, 2 operating as an evaporator) by creating a pressure drop due to flow resistance. An example of an expansion valve that can be used as the expansion valve 5 is a stepping motor-driven electronic expansion valve. In the process of adjusting the pressure by the expansion valve 5, the high-pressure liquid refrigerant sent from the condenser changes into low-temperature, low-pressure liquid refrigerant.

[0041] The refrigerant piping 6 connects the compressor 1A, the first heat exchanger 2, the second heat exchanger 3, the four-way valve 4, and the expansion valve 5 so that a refrigerant can flow between them. In this embodiment, the refrigerant piping 6 is roughly divided into a first refrigerant pipe 6a connected between the compressor 1A and the four-way valve 4, a second refrigerant pipe 6b connected between the four-way valve 4 and the first heat exchanger 2, a third refrigerant pipe 6c connected between the first heat exchanger 2 and the expansion valve 5, a fourth refrigerant pipe 6d connected between the expansion valve 5 and the second heat exchanger 3, a fifth refrigerant pipe 6e connected between the second heat exchanger 3 and the four-way valve 4, and a sixth refrigerant pipe 6f connected between the four-way valve 4 and the compressor 1A.

[0042] During cooling, the four-way valve 4 connects the inlet 4a to the first inlet / outlet 4b and connects the second inlet / outlet 4c to the outlet 4d. As a result, the refrigerant discharged from the compressor 1A flows through the four-way valve 4 to the first heat exchanger 2, is acted upon by the expansion valve 5, passes through the second heat exchanger 3, and returns to the compressor 1A via the four-way valve 4. In contrast, during heating, the four-way valve 4 switches the connection destination of the inlet 4a to the second inlet / outlet 4c and switches the connection destination of the outlet 4d to the first inlet / outlet 4b. As a result, the refrigerant discharged from the compressor 1A flows through the four-way valve 4 to the second heat exchanger 3, is acted upon by the expansion valve 5, passes through the first heat exchanger 2, and returns to the compressor 1A via the four-way valve 4.

[0043] FIG. 2 is a cross-sectional view taken along a plane including the central axis Ax1 of the sealed case (hereinafter simply referred to as the "case") 11, showing the internal configuration of the compressor 1A according to this embodiment, and FIG. 3 is a cross-sectional view taken along line AA shown in FIG. 2.

[0044] The compressor 1A includes a case 11, a motor 12, and a compression mechanism 13.

[0045] The case 11 includes a case main body 11a, a case upper portion 11b, and a case bottom portion 11c. The case main body 11a has an open upper end, a lower end integrally formed with the case bottom portion 11c, and an internal space S for accommodating the motor 12 and the compression mechanism 13. The case upper portion 11b is joined to the upper end of the case main body 11a and airtightly closes the opening at the upper end of the case main body 11a. In this embodiment, the case main body 11a and the case bottom portion 11c are integrated to form a cylindrical shape with a bottom. However, the case main body 11a and the case bottom portion 11c may be formed separately, and the case 11 may be configured from three components: the cylindrical case main body 11a, the case upper portion 11b, and the case bottom portion 11c, which are vertically penetrating. In this case, the case bottom portion 11c is joined to the lower end of the case main body 11a and airtightly closes the opening at the lower end of the case main body 11a.

[0046] In this embodiment, the case upper portion 11b is formed of a dish-shaped end plate and is joined to the case main body 11a by an appropriate method such as welding. The compressor 1A is installed vertically so that the central axis Ax1 of the case 11 is vertical, that is, so that the motor 12 and the compression mechanism 13 are stacked vertically inside the case 11.

[0047] The motor 12 is housed inside the case 11 in the upper half of the case body 11a.

[0048] The compression mechanism 13 is housed inside the case 11 in the lower half of the case body 11a.

[0049] The motor 12 constitutes a drive source for the compression mechanism 13 and includes a stator 121 and a rotor 122. The stator 121 is cylindrical and fixed to the case body 11a, while the rotor 122 is disposed on the inner diameter side of the stator 121 and is rotatably supported relative to the case body 11a.

[0050] The motor 12 has a rotor 122 connected to the compression mechanism 13 via a rotating shaft 14, and when an electromagnetic coil 121a formed in the stator 121 is energized, an electromagnetic attraction force acts on the rotor 122, causing the rotor 122 to rotate. The motor 12 then transmits the driving force in the rotational direction generated in the rotor 122 to the compression mechanism 13 via the rotating shaft 14, thereby driving the compression mechanism 13.

[0051] Here, power is supplied to the electromagnetic coil 121a of the stator 121 via a terminal portion 15 provided on the upper case 11b. The terminal portion 15 is an intermediate element that connects a lead wire (also called a "power line") (not shown) outside the case 11 that extends from a power source (for example, a commercial AC power source) of the motor 12 or a power converter such as an inverter, to a lead wire (also called an "output wire") 153 inside the case 11 that extends from the coil winding of the electromagnetic coil 121a.

[0052] In this embodiment, the terminal unit 15 includes a mounting base 151 and a plurality of terminal pins 152. The mounting base 151 is fitted into an insertion opening formed in the case upper portion 11b and is fixed to the case upper portion 11b. The terminal pins 152 have flat tab terminals fixed thereto and are attached to the mounting base 151 in a state where they penetrate the front and back of the mounting base 151. By joining the tab terminals of the terminal pins 152 to terminals of lead wires outside the case 11, it becomes possible to supply power to the electromagnetic coil 121a. The mounting base 151 ensures an insulating distance between the terminal pins 152.

[0053] The compression mechanism 13 operates using the motor 12 as a drive source, compresses the refrigerant drawn through the suction pipe 1a (hereinafter may be referred to as "suction refrigerant"), and discharges the compressed refrigerant (hereinafter may be referred to as "discharge refrigerant") through the discharge pipe 1b. In this embodiment, the compressor 1A is a sliding vane compressor, and the compression mechanism 13 roughly includes a cylinder 131, a rotor 132, a vane 133, a main bearing 134, an auxiliary bearing 135, and a discharge muffler 136.

[0054] The cylinder 131 has a cylindrical shape as a whole and is fixed to the case body 11a coaxially with the rotor 122 and the rotary shaft 14 of the motor 12. In this embodiment, the cylinder 131 has an accommodation chamber for the rotor 132 in its inner diameter portion and a discharge chamber Cd radially outward from the accommodation chamber for the rotor 132. The accommodation chamber for the rotor 132 is connected to the intake pipe 1a and the discharge chamber Cd via an intake port h1 and a discharge port h2 formed in the inner wall portion of the cylinder 131, respectively. The accommodation chamber for the rotor 132 has a substantially circular shape and is formed eccentrically with respect to the central axis of the cylinder 131 (i.e., the rotary shaft 14).

[0055] The rotor 132 is housed inside the cylinder 131 and is rotatably connected to the rotor 122 of the motor 12 via the rotary shaft 14. The rotor 132 and the rotary shaft 14 are concentric with each other and are rotatably supported by the cylinder 131.

[0056] In this embodiment, the rotor 132 is formed with a plurality of grooves g that extend radially outward and open on the outer circumferential surface of the rotor 132, and a vane 133 is housed in each of these grooves g. When the compressor 1A is in operation, the vane 133 is pressed against the inner circumferential surface of the cylinder 131 by the action of back pressure, and slides against the inner circumferential surface, thereby dividing the space between the cylinder 131 and the rotor 132 into a suction chamber Ci and a compression chamber Cc. The suction chamber Ci communicates with a suction port h1, and the compression chamber Cc communicates with a discharge port h2. The compression mechanism 13 draws in and compresses refrigerant as the rotor 132 rotates inside the cylinder 131.

[0057] 3, the cylinder 131 has a shape in which a portion of the outer periphery is cut away along a chord connecting two points on the periphery, forming a discharge chamber Cd that opens at the cut surface, and has a sealing plate 131a joined to the cut surface so as to close the discharge chamber Cd. The cylinder 131 also has a discharge valve 131b that closes the discharge port h2, and when the refrigerant inside the compression chamber Cc reaches the valve opening pressure of the discharge valve 131b, the discharge valve 131b is opened and the refrigerant flows out of the discharge port h2 into the discharge chamber Cd.

[0058] The main bearing 134 is disposed between the motor 12 and the compression mechanism 13 and supports the rotary shaft 14 .

[0059] The auxiliary bearing 135 is disposed on the opposite side of the compression mechanism 13 from the main bearing 134 , and supports the rotary shaft 14 together with the main bearing 134 .

[0060] The discharge muffler 136 is disposed concentrically with the main bearing 134, and forms a muffler chamber between the discharge muffler 136 and the main bearing 134.

[0061] After compression, the refrigerant discharged from the compression chamber Cc to the discharge chamber Cd flows into the discharge muffler 136 through a communication passage p2 formed through the cylinder 131 and the main bearing 134, and flows out into the inside of the case 11 through a circular communication port h3 formed between the inner diameter side of the discharge muffler 136 and the main bearing 134.

[0062] The refrigerant then reaches the discharge pipe 1b through the gap between the stator 121 of the motor 12 and the inner surface of the case 11, or through a connecting passage (not shown) formed in the rotor 122, and flows out of the compressor 1A through the discharge pipe 1b.

[0063] Furthermore, lubricating oil is sealed in the lower half of the case body 11a and the case bottom 11c, and the compression mechanism 13 is immersed in this lubricating oil.

[0064] In addition to the above, the compressor 1A has a gas-liquid separation chamber Cb inside the case 11.

[0065] The gas-liquid separation chamber Cb is provided around the compression chamber Cc of the compression mechanism 13, and at least a portion of it is defined by the elements that form the compression chamber Cc. The elements that form the compression chamber Cc include, for example, the cylinder 131, the rotor 132, the main bearing 134, and the auxiliary bearing 135. In this embodiment, the cylinder 131, the main bearing 134, and the auxiliary bearing 135 are used. The gas-liquid separation chamber Cb is also called a buffer chamber, and is located between the suction pipe 1a and the suction port h1 to receive the refrigerant from the suction pipe 1a and separate the refrigerant from liquid refrigerant if any is present in the refrigerant.

[0066] In this embodiment, the gas-liquid separation chamber Cb is formed outside the compression chamber Cc in the radial direction of the cylinder 131, and more specifically, is formed on the outer circumferential portion of the cylinder 131 outside the compression chamber Cc in the radial direction. That is, in this embodiment, the gas-liquid separation chamber Cb is formed in the cylinder 131 itself, and in the cross section shown in Fig. 3, the gas-liquid separation chamber Cb is entirely defined by the inner wall surface of the cylinder 131, and is isolated from the space outside the cylinder 131 in the radial direction of the cylinder 131 by the periphery of the cylinder 131. Furthermore, the gas-liquid separation chamber Cb is formed over the entire outer circumferential portion excluding the discharge chamber Cd in the circumferential direction about the central axis Ax1 of the case 11.

[0067] Furthermore, in this embodiment, the end plate portion 134a of the main bearing 134 and the end plate portion 135a of the sub-bearing 135 each extend radially outward to reach the peripheral edge of the cylinder 131, with the end plate portion 134a of the main bearing 134 contacting one axial end face of the cylinder 131 to close the accommodation chamber for the rotor 132 and also closing the gas-liquid separation chamber Cb, and the end plate portion 135a of the sub-bearing 135 contacting the other axial end face of the cylinder 131 to close the accommodation chamber for the rotor 132 and also closing the gas-liquid separation chamber Cb. With regard to each of the main bearing 134 and the sub-bearing 135, the "end plate portion" refers to a disk-shaped portion that extends radially outward from a cylindrical bearing portion that faces and supports the rotating shaft 14. In other words, the end plate portion 134a of the main bearing 134 and the end plate portion 135a of the sub-bearing 135 each have an inner circumferential portion that closes the accommodation chamber of the rotor 132 and an outer circumferential portion that closes the gas-liquid separation chamber Cb.

[0068] The sub-bearing 135 has a liquid return passage p1 formed in an end plate portion 135a that contacts the lower axial end surface of the cylinder 131, so as to straddle the inner wall portion of the cylinder 131 that defines the suction chamber Ci. In this embodiment, the liquid return passage p1 is in the form of a groove drilled in the joint surface of the end plate portion 135a, and connects the bottoms of the gas-liquid separation chamber Cb and the compression chamber Cc, allowing lubricating oil mixed in the gas-liquid separation chamber Cb to be introduced into the compression chamber Cc.

[0069] The liquid return passage p1 can be formed not only as a groove but also as a hole. For example, a hole can be formed through the inner wall of the cylinder 131 that separates the gas-liquid separation chamber Cb from the compression chamber Cc, and the gas-liquid separation chamber Cb and the compression chamber Cc can be connected to each other through this hole.

[0070] The refrigeration cycle apparatus U and the compressor 1A according to this embodiment have the above-described configurations, and the effects obtained by this embodiment will be described below.

[0071] First, by giving the compressor 1A itself the function of an accumulator, which was generally placed outside the sealed case, and by forming the gas-liquid separation chamber Cb inside the case 11, specifically around the compression chamber Cc, the space required to install an accumulator separately is reduced, making it possible to place the compressor 1A more efficiently.

[0072] Furthermore, by forming a gas-liquid separation chamber Cb around the compression chamber Cc inside the case 11, the refrigerant present in the gas-liquid separation chamber Cb can cool the compression chamber Cc, particularly the sliding parts such as the tip of the vane 133, making it possible to avoid situations where excessive heat is generated in the sliding parts or the refrigerant becomes overheated after compression.

[0073] Furthermore, the heat generated during compression, in other words, the heat transferred from the compression chamber Cc, is used to promote the vaporization of the liquid refrigerant contained in the refrigerant, reducing the amount of liquid refrigerant itself, thereby promoting gas-liquid separation and suppressing the intake of liquid refrigerant into the compression chamber Cc. By promoting the vaporization of the liquid refrigerant, the amount of refrigerant supplied to the compression chamber Cc is ensured, preventing problems such as liquid refrigerant being sucked into the compression chamber Cc or an insufficient amount of refrigerant being drawn into the compression chamber Cc.

[0074] Here, the gas-liquid separation chamber Cb is provided around the compression chamber Cc, and the gas-liquid separation chamber Cb and the compression chamber Cc are located close to each other, which makes it possible to actively utilize the heat generated during compression.

[0075] Secondly, by forming the gas-liquid separation chamber Cb outside the compression chamber Cc in the radial direction of the cylinder 131, it is possible to reduce the dimensions of the compressor 1A, for example, the height when the compressor 1A is placed vertically.

[0076] Thirdly, by forming the gas-liquid separation chamber Cb on the outer periphery of the cylinder 131, the number of parts in the compressor 1A or the compression mechanism 13 can be reduced, and the number of joints with other parts can be reduced, making it possible to easily improve the sealing performance of the gas-liquid separation chamber Cb.

[0077] Here, since the gas-liquid separation chamber Cb is located on the outer periphery of the cylinder 131, it is possible to effectively cool the compression chamber Cc formed on the inner diameter side of the cylinder 131, particularly the sliding portion between the inner periphery of the cylinder 131 and the vane 133, which is greatly affected by friction in the sliding vane type compressor 1A.

[0078] Fourth, by closing the gas-liquid separation chamber Cb with a pair of end plate portions 134a, 135a that close the axial end faces of the cylinder 131, there is no need to prepare a separate or dedicated part for closing the gas-liquid separation chamber Cb, which is economical. In addition, of the end plate portions 134a, 135a, the inner diameter portion that closes the accommodating portion of the rotor 132 and the outer diameter portion that closes the gas-liquid separation chamber Cb can be finished simultaneously in a single process that includes polishing, etc., which is advantageous in terms of processability.

[0079] Fifth, the lubricating oil mixed in the gas-liquid separation chamber Cb is introduced into the compression chamber Cc through the liquid return passage p1, which makes it possible to prevent the lubricating oil from accumulating in the gas-liquid separation chamber Cb and causing a shortage of space that actually contributes to the gas-liquid separation of the refrigerant.

[0080] Here, by forming the liquid return passage p1 in the lower end plate portion 135a or by being defined by the lower end plate portion 135a, when the compressor 1A is placed vertically, it is possible to encourage the flow of lubricating oil into the liquid return passage p1 by gravity.

[0081] Other embodiments of the present invention will be described below.

[0082] Fig. 4 is a cross-sectional view taken along a plane including the central axis Ax1 of the sealed case 11, showing the internal configuration of a compressor 1B according to another embodiment of the present invention, and Fig. 5 is a cross-sectional view taken along a plane including the central axis Ax1 of the sealed case 11 and different from that shown in Fig. 4, showing the internal configuration of the compressor 1B. In Figs. 4 and 5, elements corresponding to those of the compressor 1A according to the previous embodiment are given the same reference numerals as in Fig. 2, and repeated description will be omitted. The compressor 1B according to this embodiment can be applied to a refrigeration cycle apparatus U having a configuration similar to that shown in Fig. 1.

[0083] FIG. 6 is a partial cross-sectional view showing the configuration of the main bearing 137 of the compression mechanism 13 and its surroundings in the compressor 1B according to this embodiment.

[0084] A compressor 1B according to this embodiment will be described with reference to FIG. 6 as needed, focusing on differences from the compressor 1A according to the previous embodiment.

[0085] The compressor 1B differs from the compressor 1A according to the previous embodiment mainly in the configuration relating to the gas-liquid separation chamber Cb.

[0086] As in the previous embodiment, the gas-liquid separation chamber Cb is provided around the compression chamber Cc of the compression mechanism 13, and at least a portion of it is defined by elements that form the compression chamber Cc. In this embodiment, the gas-liquid separation chamber Cb is formed outside the compression chamber Cc in the axial direction of the cylinder 131, and radially outside the bearing portion of the main bearing 137 that supports the rotary shaft 14 of the rotor 132.

[0087] The main bearing 137 has an inner diameter portion 137a that supports the rotating shaft 14, an outer diameter portion 137b that is concentric with the inner diameter portion 137a and spaced radially outward from the inner diameter portion 137a, and a disk-shaped connecting portion 137c that connects the inner diameter portion 137a and the outer diameter portion 137b, and the gas-liquid separation chamber Cb is formed as a space surrounded by the inner diameter portion 137a, the outer diameter portion 137b, and the connecting portion 137c. In other words, the gas-liquid separation chamber Cb is shielded radially inward, radially outward, and downward by these elements 137a, 137b, and 137c of the main bearing 137, and is formed to surround the entire circumference of the inner diameter portion 137a.

[0088] Here, the inner diameter portion 137a corresponds to the bearing portion of the main bearing 137, and the connecting portion 137c functions as an end plate portion that contacts one axial end surface of the cylinder 131 and closes the accommodation chamber of the rotor 132. That is, in this embodiment, the accommodation chamber of the rotor 132 is sealed in the axial direction by the connecting portion 137c of the main bearing 137 and the end plate portion 135a of the sub-bearing 135.

[0089] Furthermore, the main bearing 137 is configured such that an opening is provided in the outer diameter portion 137b, and the suction pipe 1a is connected to this opening, thereby receiving the refrigerant from the suction pipe 1a into the gas-liquid separation chamber Cb.

[0090] An end plate 138 is attached to the shaft end surface that opens upward relative to the main bearing 137, and the gas-liquid separation chamber Cb is closed by this end plate 138 from above.

[0091] In addition to the above, in this embodiment, a communication passage p3 that connects the gas-liquid separation chamber Cb and the suction port h1 is formed in the outer diameter portion 137b of the main bearing 137, and a communication port h4 that penetrates the inner wall portion of the main bearing 137 that defines the communication passage p3 and connects the gas-liquid separation chamber Cb and the communication passage p3 is formed.

[0092] The communicating passage p3 is formed as a cylindrical space extending parallel to the axial direction of the cylinder 131, terminating near the axial end of the main bearing 137, and forming a small gap g1 between it and the end plate 138. The opening area of ​​this gap g1 makes it possible to adjust the flow resistance or fluid loss of the refrigerant from the gas-liquid separation chamber Cb to the suction port h1. By extending the communicating passage p3 close to the end plate 138 without excessively increasing the flow resistance, the amount of liquid refrigerant that can be stored can be increased, and combined with the effect of heat from the compression chamber Cc, it is possible to promote evaporation of the liquid refrigerant.

[0093] In this embodiment, as shown in Fig. 6, a volume portion connected to the suction port h1, i.e., a suction chamber Cs, is formed on the outer periphery of the cylinder 131, and a communication passage p3 of the main bearing 137 is connected to this suction chamber Cs. As a result, refrigerant (particularly the gaseous refrigerant after gas-liquid separation) that flows from the gas-liquid separation chamber Cb into the communication passage p3 is introduced into the suction chamber Cs and is drawn from the suction chamber Cs through the suction port h1 into the suction chamber Ci between the cylinder 131 and the rotor 132. In Fig. 6, arrow a1 indicates the flow of refrigerant flowing from the suction pipe 1a into the gas-liquid separation chamber Cb, arrow a2 indicates the flow of refrigerant flowing from the gas-liquid separation chamber Cb into the communication passage p3, arrow a3 indicates the flow of refrigerant flowing from the communication passage p3 into the suction chamber Cs, and arrow a4 indicates the flow of refrigerant flowing from the suction chamber Cs into the suction chamber Ci through the suction port h1.

[0094] The communication port h4 forms a liquid return passage, allowing the liquid refrigerant after gas-liquid separation and the lubricating oil mixed in the gas-liquid separation chamber Cb to escape to the communication passage p3 and be introduced into the compression chamber Cc. In Figure 6, arrows a5 indicate the flow of the liquid refrigerant and lubricating oil flowing from the gas-liquid separation chamber Cb into the communication passage p3 via the communication port h4.

[0095] FIG. 9 is a partial cross-sectional view showing a support structure for the compression mechanism 13 in the compressor 1B according to this embodiment.

[0096] In this embodiment, a press bolt 140 is used as a fastener for the compression mechanism 13. Specifically, a through-hole is formed that penetrates both the cylinder 131 and the end plate portion 135a of the sub-bearing 135 from below and reaches the connecting portion 137c of the main bearing 137, and a female thread is formed on the inner periphery of the hole in the connecting portion 137c. The press bolt 140 is then inserted from below into the end plate portion 135a and then the cylinder 131, and is screwed into the female thread of the connecting portion 137c. In this way, the cylinder 131 and the sub-bearing 135 are fastened together to the main bearing 137 and fixed. By fixing the main bearing 137 to the case 11, the entire compression mechanism 13 can be fixed to the case 11.

[0097] In this way, by forming the gas-liquid separation chamber Cb outside the compression chamber Cc in the axial direction of the cylinder 131, it is possible to reduce the dimensions of the compressor 1B, for example, the installation area when the compressor 1B is placed vertically.

[0098] Here, by forming the gas-liquid separation chamber Cb radially outward from the bearing portion that supports the rotating shaft 14 of the rotor 132, specifically the inner diameter portion 137a of the main bearing 137, it may be necessary to extend the length of the rotating shaft 14, but it is possible to form the gas-liquid separation chamber Cb by effectively utilizing the space between the motor 12 and the compression mechanism portion 13 and without increasing the installation area of ​​the compressor 1B. In other words, it becomes easy to ensure the space for forming the gas-liquid separation chamber Cb.

[0099] By forming an inner diameter portion 137a, an outer diameter portion 137b, and a connecting portion 137c in the main bearing 137, and forming the gas-liquid separation chamber Cb as a space surrounded by the inner diameter portion 137a, the outer diameter portion 137b, and the connecting portion 137c, it is possible to easily ensure the sealing of the gas-liquid separation chamber Cb, particularly the sealing of the compression chamber Cc.

[0100] The refrigerant present in the gas-liquid separation chamber Cb can be introduced into the compression chamber Cc through the communication passage p3. Here, by forming the communication passage p3 in the main bearing 137, specifically in the outer diameter portion 137b thereof, there is no need to prepare a special member for forming the communication passage p3, which is economical and ensures resistance to thermal shock when liquid refrigerant gets mixed into the gas-liquid separation chamber Cb.

[0101] By fixing the cylinder 131 and the sub-bearing 135 to the main bearing 137 by fastening them together with the pressure bolt 140, it is possible to avoid a situation in which the sealing of the gas-liquid separation chamber Cb is impaired due to the use of fasteners, and to suppress the effect on the bolt axial force when liquid refrigerant gets mixed into the gas-liquid separation chamber Cb.

[0102] In this embodiment, the communication passage p3 of the main bearing 137 that connects the gas-liquid separation chamber Cb and the suction port h1 is formed by the inner wall portion of the main bearing 137 (FIG. 6). The formation of the communication passage p3 is not limited to this, and it can also be formed by a dedicated member.

[0103] FIG. 7 is a partial cross-sectional view showing the configuration of the main bearing 137 of the compression mechanism 13 and its surroundings in a compressor according to a first modified example of the present embodiment.

[0104] In the first modified example, a cylindrical member 139 separate from the main bearing 137 is used and embedded in the outer diameter portion 137b of the main bearing 137 to form a communication passage p3. The cylindrical member 139 terminates near the axial end of the main bearing 137, forming a small gap g2 between the cylindrical member 139 and the end plate 138. A hole h5 is formed radially through the wall of the cylindrical member 139, connecting the gas-liquid separation chamber Cb to the interior of the cylindrical member 139, i.e., the communication passage p3. In other words, the through hole h5 replaces the communication port h4 in the previous example and forms a liquid return passage. In FIG. 7, arrow a6 indicates the flow of liquid refrigerant and lubricant flowing from the gas-liquid separation chamber Cb through the through hole h5 into the communication passage p3. In FIG. 7, the other arrows a1 to a4 indicate the same flows as in FIG. 6.

[0105] In this way, by forming the communicating passage p3 using a member separate from the main bearing 137, it becomes possible to change the dimensions of the communicating passage p3 as appropriate depending on the refrigerant flow rate, the required amount of liquid refrigerant to be stored, etc. In particular, by individually adjusting the cylindrical member 139, it is possible to optimize or minimize fluid loss in the communicating passage p3, and to minimize the adverse effects that the formation of the gas-liquid separation chamber Cb has on the operating performance of the compressor.

[0106] Furthermore, the liquid return passage may be formed not only in the inner wall portion of the main bearing 137 that forms the communication passage p3 or in a separate member, but also in the connecting portion 137c or the end plate portion.

[0107] FIG. 8 is a partial cross-sectional view showing the configuration of the main bearing 137 of the compression mechanism 13 and its surroundings in a compressor according to a second modified example of the present embodiment.

[0108] In the second modification, a hole p4 is formed as a liquid return passageway, vertically penetrating the connecting portion 137c of the main bearing 137, and the gas-liquid separation chamber Cb communicates with the intake port h1 or the suction chamber Cs via this through hole p4.

[0109] In this way, by forming through hole p4 in connecting portion 137c of main bearing 137 and connecting gas-liquid separation chamber Cb with suction port h1 or suction chamber Cs, the negative pressure generated in suction chamber Ci is more directly transmitted to gas-liquid separation chamber Cb, making it possible to more actively discharge lubricating oil and liquid refrigerant accumulated in gas-liquid separation chamber Cb from gas-liquid separation chamber Cb. In Figure 8, arrows a7 indicate the flow of lubricating oil and liquid refrigerant flowing from gas-liquid separation chamber Cb into suction chamber Cs through through hole p4.

[0110] In the above description, sliding vane compressors are used as the compressors 1A and 1B, but the compressors that can be used are not limited to this, and rolling piston compressors may also be used.

[0111] Although several embodiments of the present invention have been described, these embodiments are presented merely as examples and are not intended to limit the scope of the invention. These novel embodiments can be embodied in various other forms, and various omissions, substitutions, modifications, etc. can be made without departing from the spirit of the invention. These embodiments and their modifications are included within the scope and spirit of the invention, and are also included in the inventions and their equivalents as set forth in the claims. [Explanation of symbols]

[0112] U...refrigeration cycle device, 1A, 1B...compressor, 1a...suction pipe, 1b...discharge pipe, 11...sealed case, 12...motor, 121...stator, 122...rotor, 13...compression mechanism, 131...cylinder, 132...rotor, 133...vane, 134...main bearing, 135...auxiliary bearing, 136...discharge muffler, 14...rotating shaft, 2...first heat exchanger, 3...second heat exchanger, 4...four-way valve, 5...expansion valve, 6 (6a to 6f)...refrigerant piping, h1...suction port, h2...discharge port, Ci...suction chamber, Cc...compression chamber, Cb...gas-liquid separation chamber, S...space inside the case.

Claims

1. Case and a motor housed in the case; a compression mechanism portion housed in the case and configured to be drivable by the motor, the inside of the case is a high-pressure atmosphere filled with the refrigerant compressed by the compression mechanism; The compression mechanism portion is provided with a gas-liquid separation chamber around the compression chamber, the gas-liquid separation chamber being at least partially defined by an element that forms the compression chamber, and separating the refrigerant drawn into the compression chamber into a gas refrigerant and a liquid refrigerant; a liquid return passage that opens to a lower portion of the gas-liquid separation chamber when the compressor is installed, communicates with the compression chamber, and is capable of introducing lubricating oil that has entered the gas-liquid separation chamber into the compression chamber.

2. The compressor is A cylindrical cylinder; a rotor rotatably disposed on the inner diameter side of the cylinder; a vane disposed between the cylinder and the rotor so as to be movable in a radial direction relative to the rotor, the vane dividing a space between the cylinder and the rotor into a suction chamber and a compression chamber, The compressor according to claim 1 , wherein the gas-liquid separation chamber is formed outside the compression chamber in a radial direction of the cylinder.

3. The compressor according to claim 2 , wherein the gas-liquid separation chamber is formed in an outer peripheral portion of the cylinder, the outer peripheral portion being outside the compression chamber in the radial direction.

4. the compressor further includes a pair of end plate portions disposed in contact with both ends of the cylinder in the axial direction, Each of the end plates is an inner diameter portion that closes a space of the cylinder in which the rotor is accommodated; The compressor according to claim 3 , further comprising an outer diameter portion that closes the gas-liquid separation chamber.

5. The compressor is installed vertically so that the motor is located above the compression mechanism, 5. The compressor according to claim 4, wherein the liquid return passage is formed in a surface of the lower end plate portion that contacts the end surface of the cylinder, or is defined by the lower end plate portion.

6. The compressor is A cylindrical cylinder; a rotor rotatably disposed on the inner diameter side of the cylinder; a vane disposed between the cylinder and the rotor so as to be movable in a radial direction relative to the rotor, the vane dividing a space between the cylinder and the rotor into a suction chamber and a compression chamber, The compressor according to claim 1 , wherein the gas-liquid separation chamber is formed outside the compression chamber in the axial direction of the cylinder.

7. the compressor further includes a bearing disposed outside the compression chamber with respect to the axial direction, the bearing has a bearing portion that supports a rotation shaft of the rotor, The compressor according to claim 6, wherein the gas-liquid separation chamber is formed radially outward of the bearing portion.

8. The bearing is an inner diameter portion serving as the bearing portion that supports the rotation shaft of the rotor; an outer diameter portion provided concentrically with the inner diameter portion and spaced apart radially outward from the inner diameter portion; a connecting portion connecting the inner diameter portion and the outer diameter portion, The compressor according to claim 7, wherein the gas-liquid separation chamber is formed as a space surrounded by the inner diameter portion, the outer diameter portion, and the connecting portion.

9. 9. The compressor according to claim 8, wherein the bearing further includes a communication passage that connects the gas-liquid separation chamber with the compression chamber and that allows the gas refrigerant present in the gas-liquid separation chamber to be introduced into the compression chamber.

10. The compressor is an end plate portion disposed in contact with a lower end of the cylinder in the axial direction and closing a space of the cylinder from below in which the rotor is housed; 8. The compressor according to claim 7, further comprising a press bolt that passes through the end plate portion and the cylinder from below in the axial direction, reaches the bearing, and fastens the end plate portion and the cylinder together to the bearing.

11. A compressor according to any one of claims 1 to 10; A condenser; An expansion valve; an evaporator; a refrigerant pipe that connects the compressor, the condenser, the expansion valve, and the evaporator, and circulates the refrigerant discharged from the compressor through the condenser, the expansion valve, and the evaporator.

Images