Compressors and refrigeration cycle equipment

Abstract

This invention provides a highly reliable compressor and refrigeration cycle device by suppressing the reduction in lubrication between the tip surface of the blade and the outer surface of the roller. [Solution] The compressor 2 comprises a sealed container 11, a compression mechanism 13 disposed inside the sealed container 11 and capable of compressing a refrigerant, an electric motor 12 disposed inside the sealed container 11 and driving the compression mechanism 13, and a crankshaft having an eccentric portion 26 that is eccentric from the rotation centerline C and that transmits the rotational driving force of the electric motor 12 to the compression mechanism 13. The compression mechanism 13 comprises a cylinder 32 having a circular cylinder chamber 31 inside, a roller 33 fitted onto the eccentric portion 26 and disposed in the cylinder chamber 31, and a blade 34 that contacts the roller 33 and divides the cylinder chamber 31 into a suction chamber 31s and a compression chamber 31c. The blade 34 includes a plurality of segmented blades 51 that are arranged adjacent to each other in the circumferential direction of the cylinder chamber 31.

Description

Technical Field

[0001] Embodiments of the present invention relate to a compressor and a refrigeration cycle device.

Background Art

[0002] A rotary compressor having a sealed case, a motor unit housed in the sealed case, a compression mechanism unit housed in the sealed case, and a rotating shaft connecting the motor unit and the compression mechanism unit is known. The compression mechanism unit of this compressor includes a cylinder having a cylinder chamber, a roller that eccentrically moves in the cylinder chamber, and a vane that abuts against the roller and partitions the cylinder chamber into a compression chamber and a suction chamber. The vane includes two divided vanes arranged one above the other in the height direction of the cylinder, which is the axial direction of the rotating shaft. The two divided vanes reduce the amount of gas refrigerant leaking from the compression chamber side to the suction chamber side in the cylinder chamber and suppress an increase in leakage loss. Also, the two divided vanes suppress an increase in sliding loss between the vane and the roller due to deflection of the rotating shaft. The vane is also called a blade. The rotating shaft is also called a crankshaft.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] Generally, a blade is a single plate-like component, and during compressor operation, the entire back surface of the blade is subjected to the high discharge pressure of the gaseous refrigerant filling the sealed container. At this time, a back load proportional to the area of ​​the back surface of the blade acts on the blade. Depending on the operating conditions of the compressor, this back load may act significantly on the tip surface of the blade. When a large back load acts on the tip surface of the blade, the oil film formed by lubricating oil (refrigerant oil) between the tip surface of the blade and the outer surface of the roller becomes excessively thin or breaks, resulting in oil film breakdown. Oil film breakdown reduces the lubrication between the tip surface of the blade and the outer surface of the roller, which may cause abnormal wear on both surfaces.

[0005] Therefore, the present invention aims to provide a compressor and refrigeration cycle device that suppress the decrease in lubricity between the tip surface of the blade and the outer surface of the roller, and that offer superior reliability. [Means for solving the problem]

[0006] To solve the aforementioned problems, a compressor according to an embodiment of the present invention comprises a sealed container, a compression mechanism disposed within the sealed container and capable of compressing a refrigerant, an electric motor disposed within the sealed container and driving the compression mechanism, and a crankshaft having an eccentric portion offset from the rotational centerline and transmitting the rotational driving force of the electric motor to the compression mechanism. The compression mechanism comprises a cylinder having a circular cylinder chamber inside, a roller fitted onto the eccentric portion and disposed in the cylinder chamber, and a blade that contacts the roller and divides the cylinder chamber into a suction chamber and a compression chamber. The blade includes a plurality of segmented blades arranged adjacent to each other in the circumferential direction of the cylinder chamber.

[0007] Furthermore, in order to solve the above-mentioned problems, the refrigeration cycle apparatus according to the embodiment of the present invention comprises a compressor, a heat sink, an expansion device, a heat absorber, and refrigerant piping that connects the compressor, the heat sink, the expansion device, and the heat absorber and allows the refrigerant to flow. [Brief explanation of the drawing]

[0008] [Figure 1] A schematic diagram of a refrigeration cycle device and compressor according to an embodiment of the present invention. [Figure 2] Cross-sectional view AA in Figure 1. [Figure 3] A schematic diagram showing the compression process of a compression mechanism provided in an embodiment of the present invention. [Figure 4] A schematic diagram showing the pressure and force acting on the blades in a compressor according to an embodiment of the present invention. [Figure 5] A schematic diagram showing the pressure and force acting on a comparative example of blades in a compressor according to an embodiment of the present invention. [Figure 6] (A) A schematic plan view showing the blades of the compression mechanism of a compressor according to an embodiment of the present invention; (B) A schematic side view showing the blades of the compression mechanism of a compressor according to an embodiment of the present invention; (C) A schematic plan view showing a comparative example of the blades of the compression mechanism of a compressor according to an embodiment of the present invention. [Figure 7] A schematic enlarged view of region Q1 in Figure 2. [Modes for carrying out the invention]

[0009] The compressor and refrigeration cycle device according to this embodiment will be described with reference to Figures 1 to 7. Note that the same or corresponding components in multiple drawings are denoted by the same reference numerals.

[0010] Figure 1 is a schematic diagram of a refrigeration cycle device and compressor according to an embodiment of the present invention.

[0011] As shown in Figure 1, the refrigeration cycle device 1 according to this embodiment includes a sealed rotary compressor 2, a heat sink 3, an expansion device 5, a heat absorber 6, an accumulator 7, and refrigerant piping 8. The refrigerant piping 8 sequentially connects the compressor 2, the heat sink 3, the expansion device 5, the heat absorber 6, and the accumulator 7 to circulate the refrigerant. Hereinafter, the rotary compressor 2 may be simply referred to as the compressor 2.

[0012] The compressor 2 draws in the refrigerant that has passed through the heat absorber 6 via the refrigerant piping 8, compresses it via the accumulator 7, and discharges the high-temperature, high-pressure refrigerant to the heat radiator 3 through the refrigerant piping 8.

[0013] The compressor 2 comprises a vertically positioned cylindrical sealed container 11, an electric motor 12 located in the upper half of the sealed container 11, a compression mechanism 13 located in the lower half of the sealed container 11, a crankshaft 15 that transmits the rotational driving force of the electric motor 12 to the compression mechanism 13, a main bearing 16 that rotatably supports the crankshaft 15, and a sub-bearing 17 that cooperates with the main bearing 16 to rotatably support the crankshaft 15.

[0014] The sealed container 11 comprises a cylindrical body 11a extending vertically, a hemispherical or elliptical upper end plate 11b that closes the upper end of the body 11a, and a hemispherical or elliptical lower end plate 11c that closes the lower end of the body 11a. The centerline of the sealed container 11 substantially coincides with the rotational centerline C of the crankshaft 15.

[0015] The lower part of the sealed container 11 is filled with lubricating oil (refrigerating oil), which is not shown in the diagram. Most of the compression mechanism 13 is immersed in the lubricating oil inside the sealed container 11.

[0016] The upper end plate 11b of the sealed container 11 is equipped with a discharge pipe 8a for discharging refrigerant. The discharge pipe 8a is connected to the refrigerant piping 8. The upper end plate 11b is also equipped with a sealed terminal section (not shown) for power supply. The shell 11a is equipped with a suction pipe 7a for drawing in refrigerant, which is connected to the compression mechanism 13.

[0017] The electric motor 12 generates a driving force to rotate the compression mechanism 13. The electric motor 12 is, for example, a permanent magnet synchronous motor of the embedded magnet type. The electric motor 12 comprises a cylindrical stator 21 fixed to the inner wall of the sealed container 11, a rotor 22 positioned inside the stator 21 and fixed to the crankshaft 15, and a plurality of lead wires (not shown) drawn out from the stator 21 and connected to the sealed terminal section.

[0018] The stator 21 is a concentrated winding stator. The stator 21 includes a yoke (not shown) which is a cylindrical armature core, a stator core 23 having a plurality of teeth (not shown) that project inward of the yoke and are arranged in the circumferential direction at intervals, a plurality of insulating end plates 24A and 24B provided on respective end faces 23a and 23b of the stator core 23, windings (not shown) wound around respective teeth and the insulating end plates 24A and 24B, and a plurality of insulating sheets (not shown) sandwiched between respective windings and respective teeth.

[0019] The rotor 22 includes a rotor core 25 having a magnet accommodation hole (not shown) and a permanent magnet (not shown) accommodated in the magnet accommodation hole. The rotor 22 is fixed to the crankshaft 15. The rotation center line C of the rotor 22 and the crankshaft 15 substantially coincides with the center line of the stator 21. In the following description, the direction along the rotation center line C may be referred to as the axial direction, the direction of rotation around the rotation center line C may be referred to as the circumferential direction, and the direction orthogonal to the axial direction and the circumferential direction may be referred to as the radial direction.

[0020] The plurality of lead-out lines are wirings for supplying power to the stator 21 through the sealed terminal portion and are so-called lead wires. The lead-out lines are wired in plurality according to the type of the electric motor 12. When the lead-out lines are used in an open-winding type, two lead-out lines are wired for each of the U-phase, V-phase, and W-phase, that is, a total of six lead-out lines are wired. When the electric motor 12 is used in a star connection, one lead-out line is wired for each of the U-phase, V-phase, and W-phase, that is, a total of three lead-out lines are wired.

[0021] The crankshaft 15 connects the electric motor 12 and the compression mechanism 13. The crankshaft 15 transmits the rotational driving force generated by the electric motor 12 to the compression mechanism 13.

[0022] An intermediate portion 15a of the crankshaft 15 connects the electric motor 12 and the compression mechanism 13 and is rotatably supported by a main bearing 16. A lower end portion 15b of the crankshaft 15 is rotatably supported by a sub-bearing 17. The main bearing 16 and the sub-bearing 17 are also part of the compression mechanism 13. In other words, the crankshaft 15 penetrates the compression mechanism 13.

[0023] Furthermore, the crankshaft 15 has an eccentric portion 26 that is eccentric from the rotational centerline C between the intermediate portion 15a supported by the main bearing 16 and the lower end portion 15b supported by the sub-bearing 17. The eccentric portion 26 is a disc or cylinder whose center is not aligned with the rotational centerline C.

[0024] The compression mechanism 13 can compress refrigerant, i.e., a single refrigerant or a mixture of refrigerants. The electric motor 12 rotates the crankshaft 15, causing the compression mechanism 13 to draw in gaseous refrigerant from the suction pipe 7a, compress it, and discharge it into the sealed container 11.

[0025] Figure 2 is a cross-sectional view along line AA in Figure 1.

[0026] As shown in Figure 2 in addition to Figure 1, the compression mechanism 13 comprises a cylinder 32 having a circular cylinder chamber 31, an annular roller 33 positioned inside the cylinder chamber 31, and a blade 34 that reciprocates in contact with the outer circumferential surface 33a of the roller 33, dividing the inside of the cylinder chamber 31 into a suction chamber 31s and a compression chamber 31c.

[0027] In this embodiment, the compression mechanism 13 is a single-cylinder rotary compression mechanism. However, it is not limited to this, and the compression mechanism 13 may be a rotary compression mechanism with two or more cylinders. In other words, the compressor 2 may be a single-cylinder rotary compressor or a multi-cylinder rotary compressor.

[0028] The cylinder 32 has a circular shape with its outer circumference partially cut out when viewed in the direction along the centerline of the cylinder chamber 31, that is, in the axial direction. The cylinder 32 has an inner circumferential surface that defines the cylinder chamber 31. The cylinder 32 has an annular, plate-like shape with the cylinder chamber 31 inside. The cylinder 32 has an end face closer to the electric motor 12 and an end face further away from the electric motor 12.

[0029] Furthermore, the cylinder 32 has a suction port 35 connected to the suction pipe 7a and reaching the cylinder chamber 31, a discharge port 36 connected to the cylinder chamber 31, a blade groove 37 in which the blades 34 are positioned, and a blade back pressure chamber 39 connected to the blade groove 37. The suction port 35 guides the gaseous refrigerant discharged from the accumulator 7 into the cylinder chamber 31 via the suction pipe 7a. The discharge port 36 guides the compressed refrigerant, which is the refrigerant compressed in the cylinder chamber 31, into the sealed container 11.

[0030] The suction pipe 7a passes through the sealed container 11 and is connected to the cylinder chamber 31 via the suction port 35 of the cylinder 32.

[0031] The blade groove 37 has one end that is open into the cylinder chamber 31 and the other end that is connected to the blade back pressure chamber 39. The blade groove 37 is provided on the cylinder 32 and extends linearly in the radial direction of the cylinder 32, that is, in the radial direction of the cylinder chamber 31.

[0032] The blade back pressure chamber 39 is open to the sealed container 11. That is, the blade back pressure chamber 39 is under the atmosphere of high-pressure gaseous refrigerant discharged from the compression mechanism 13. The blade back pressure chamber 39 houses a blade spring 40, which is arranged in series with the blade 34 and is partially omitted in the illustration. The blade spring 40 is in contact with the blade 34 and applies force to press the tip surface of the blade 34 against the outer circumferential surface 33a of the roller 33. The blade spring 40 is, for example, a coil spring.

[0033] The cylinder chamber 31 is the space inside the cylinder 32 and is closed off by the main bearing 16 and the sub-bearing 17. The cylinder chamber 31 houses the eccentric portion 26 of the crankshaft 15.

[0034] The main bearing 16 is provided with a discharge valve mechanism 42 for discharging the refrigerant compressed in the cylinder chamber 31, and a discharge muffler 43 that covers the discharge valve mechanism 42. The discharge valve mechanism 42 opens the discharge port 36 when the pressure difference between the pressure in the cylinder chamber 31 and the pressure in the discharge muffler 43 reaches a predetermined value due to the compression action of the compression mechanism 13, and discharges the compressed refrigerant into the discharge muffler 43. The discharge muffler 43 has a discharge hole (not shown) that connects the inside and outside of the discharge muffler 43. The compressed refrigerant discharged into the discharge muffler 43 is discharged into the sealed container 11 through the discharge hole.

[0035] The discharge muffler 43, main bearing 16, cylinder 32, and sub-bearing 17 are integrated by fastening members 41 such as bolts that pass through them. The main bearing 16 is fixed to the sealed container 11 by welding, for example, spot welding, at appropriate points in the circumferential direction. The entire compression mechanism 13 is supported by the welded points of the main bearing 16 to the sealed container 11.

[0036] The roller 33 is fitted onto the outer circumferential surface of the eccentric portion 26. The outer circumferential surface 33a of the roller 33 is in line contact with the inner circumferential surface of the cylinder chamber 31 via a lubricating oil film. As the crankshaft 15 rotates, the roller 33 undergoes eccentric motion while its outer circumferential surface 33a is in line contact with the inner circumferential surface of the cylinder chamber 31 via a lubricating oil film.

[0037] Figure 3 is a schematic diagram showing the compression process of the compression mechanism of a compressor according to an embodiment of the present invention.

[0038] In Figure 3, state S1 shows the case where the rotation angle of the crankshaft 15 is 0 degrees (°). The position of the roller 33 in the cylinder chamber 31 at this rotation angle of 0 degrees is called the top dead center. When the roller 33 is at the top dead center, the blade 34 is completely retracted into the blade groove 37. State S2 shows the case where the rotation angle of the crankshaft 15 is 90 degrees. State S3 shows the case where the rotation angle of the crankshaft 15 is 180 degrees. The position of the roller 33 in the cylinder chamber 31 at this rotation angle of 180 degrees is called the bottom dead center. When the roller 33 is at the bottom dead center, the blade 34 protrudes the furthest into the cylinder chamber 31 from the blade groove 37. State S4 shows the case where the rotation angle of the crankshaft 15 is 270 degrees. The rotation angle of the crankshaft 15 in Figure 3 is the rotation angle when the rotation direction R is the forward rotation direction.

[0039] The blade 34 is positioned in the blade groove 37 and reciprocates radially within the cylinder chamber 31 while being pressed against the roller 33 by a blade spring 40 provided in the blade back pressure chamber 39. The blade 34 divides the space between the cylinder 32 and the roller 33 into two in this radial direction. In other words, the blade 34 divides the inside of the cylinder chamber 31 into an intake chamber 31s and a compression chamber 31c in this radial direction. As shown in Figure 3, during the series of compression steps from state S1 to S4, the blade 34 is always in contact with the outer circumferential surface 33a of the roller 33 via an oil film, regardless of the rotation angle of the crankshaft 15.

[0040] Although the contact between the blade 34 and the roller 33 is not direct but indirect, mediated by a lubricating oil film, for the sake of explanation, this contact mediated by the oil film will simply be referred to as "contact." The same applies to the contact between the roller 33 and the cylinder 32, between the roller 33 and the eccentric portion 26, between the roller 33 and the main bearing 16, and between the roller 33 and the sub-bearing 17.

[0041] Figure 4 is a schematic diagram showing the pressure and force acting on the blades in a compressor according to an embodiment of the present invention.

[0042] Note that Figure 4 shows the case where the rotation angle of the crankshaft 15 is 270 degrees (see state S3 in Figure 3). The same applies to Figure 5, which will be explained later.

[0043] Figure 5 is a schematic diagram showing the pressure and force acting on a comparative example of blades in a compressor according to an embodiment of the present invention.

[0044] Note that blade 34C, which is a comparative example of blade 34 shown in Figure 5, is a single plate member.

[0045] Figure 6(A) is a schematic plan view showing the blades of the compression mechanism of a compressor according to an embodiment of the present invention, Figure 6(B) is a schematic side view showing the blades of the compression mechanism of a compressor according to an embodiment of the present invention, and Figure 6(C) is a schematic plan view showing a comparative example of the blades of the compression mechanism of a compressor according to an embodiment of the present invention. Note that the side view of blade 34C, which is a comparative example of blade 34, has the same dimensions as the side view of blade 34, so its illustration is omitted.

[0046] Generally, a compressor blade is a single plate-like component, and during compressor operation, the entire back surface of the blade is subjected to the high discharge pressure of the gaseous refrigerant filling the sealed container. At this time, a back load proportional to the area of ​​the back surface of the blade acts on it. If the back load acts heavily on the tip surface of the blade, oil film breakdown occurs between the tip surface of the blade and the outer surface of the roller, reducing lubrication (sliding performance). Oil film breakdown causes abnormal wear on the tip surface of the blade and the outer surface of the roller, which can lead to a decrease in compressor performance and ultimately to the shutdown of the compressor.

[0047] Therefore, as shown in Figure 4 in addition to Figure 2, the blade 34 includes a plurality of segmented blades 51 that are arranged adjacent to each other in the circumferential direction of the cylinder 32, that is, in the circumferential direction of the cylinder chamber 31. In other words, the blade 34 includes a plurality of segmented blades 51 that are superimposed in a direction perpendicular to the radial direction of the cylinder chamber 31. Each segmented blade 51 is a relatively thin plate member.

[0048] Specifically, as shown in Figures 5, 6(B), and 6(C), a comparative example of blade 34, blade 34C, which is a single plate member, receives a high discharge pressure Pd on its back surface 34Cb, and a back surface load Fb1 acts on blade 34C. The discharge pressure Pd is the pressure of the gaseous refrigerant discharged from the discharge muffler 43 to fill the sealed container 11. The back surface load Fb1 increases in proportion to the area of ​​the back surface 34Cb. The area of ​​the back surface 34Cb is substantially obtained by multiplying the thickness t1 of blade 34C by its height H. When the back surface load Fb1 acts strongly on the tip surface 34Ct of blade 34C, oil film breakdown occurs between the tip surface 34Ct of blade 34C and the outer peripheral surface 33a of roller 33, reducing lubricity.

[0049] On the other hand, as shown in Figures 6(A) and 6(B), in addition to Figures 2 and 4, each of the multiple segmented blades 51 in this embodiment receives a discharge pressure Pd on its back surface 51b, and a back surface load Fb2 acts on each of the multiple segmented blades 51. The area of ​​the back surface 51b of the segmented blade 51 is substantially obtained by multiplying the thickness t2 of the segmented blade 51 by its height H. Since the dimension of thickness t2 is smaller than the dimension of thickness t1, the back surface load Fb2 received by the segmented blade 51 is smaller than the back surface load Fb1 received by the blade 34C. In other words, the multiple segmented blades 51 distribute and receive the high-pressure discharge pressure Pd of the gaseous refrigerant in the sealed container 11 on their respective back surfaces 51b. As a result, the multiple segmented blades 51 reduce the load that presses their respective front surfaces 51t against the outer circumferential surface 33a of the roller 33 from their respective back surfaces 51b. In other words, the reduction in lubrication is suppressed when the tip surface of the blade 34, that is, the tip surface 51t of each segmented blade 51, comes into contact with the outer circumferential surface 33a of the roller 33. Therefore, the multiple segmented blades 51 suppress abnormal wear of the tip surface of the blade 34 and the outer circumferential surface 33a of the roller 33 caused by reduced lubrication, thereby improving the reliability of the compressor 2.

[0050] In this embodiment, there are two segmented blades 51. However, the number of segmented blades 51 is not limited to two; there may be three or more segmented blades 51, as long as the function and rigidity of the blades are not compromised. Furthermore, each of the segmented blades 51 is movable in the radial direction of the cylinder chamber 31 along the outer circumferential surface 33a of the roller 33. In other words, adjacent segmented blades 51 are in sliding contact with each other.

[0051] Here, referring again to Figures 4 and 5, the pressure acting on the tip surface of blade 34 in this embodiment and the tip surface 34Ct of blade 34C in the comparative example will be explained.

[0052] As shown in Figure 4, the following pressures act on the tip surfaces 51t of each of the multiple segmented blades 51 of the blade 34. A low suction pressure Ps and an intermediate pressure Pm act on the suction chamber 31s side, with the contact line between the tip surface 51t of the segmented blade 51 located on the suction chamber 31s side and the outer surface 33a of the roller 33 as the boundary. In addition, an intermediate pressure Pm and a compression pressure Pd' act on the compression chamber 31c side, with the contact line between the tip surface 51t of the segmented blade 51 located on the compression chamber 31c side and the outer surface 33a of the roller 33 as the boundary. The intermediate pressure Pm is the pressure that acts on the tip surface 51t when a small amount of gaseous refrigerant in the compression chamber 31c side leaks out to the suction chamber 31s side. Here, the following relationship (1) holds for the suction pressure Ps, intermediate pressure Pm, compression pressure Pd', and discharge pressure Pd. Ps <Pm<Pd′<Pd (1)

[0053] The back load Fb2 on the back surface 51b of the split blade 51 is greater than the load on the front surface 51t of the split blade 51, and the front surface 51t is pressed against the outer surface 33a of the roller 33 with a predetermined load.

[0054] Furthermore, as shown in Figure 5, in the case of blade 34C, which is a comparative example of blade 34, the tip surface 34Ct of blade 34C is subjected to a low-pressure suction pressure Ps on the suction chamber 31s side and a compression pressure Pd' on the compression chamber 31c side, with the contact line between the tip surface 34Ct and the outer peripheral surface 33a of the roller 33 as the boundary. Here, the following relationship (2) holds for the suction pressure Ps, the compression pressure Pd', and the discharge pressure Pd. Ps <Pd′<Pd (2)

[0055] The back load Fb1 on the back surface 34Cb of the blade 34C is greater than the load on the front surface 34Ct, and the front surface 34Ct of the blade 34C is pressed against the outer surface 33a of the roller 33 with a predetermined load.

[0056] Furthermore, the sum of the loads that the entire tip surface of blade 34 receives from the suction pressure Ps, the intermediate pressure Pm, and the pressure Pd' during compression is substantially the same as the sum of the loads that the entire tip surface 34Ct of blade 34C receives from the suction pressure Ps and the pressure Pd' during compression.

[0057] Furthermore, unlike blade 34C, blade 34 consists of multiple segmented blades 51, each with a reduced thickness, stacked in the circumferential direction of the cylinder chamber 31. This prevents a decrease in the rigidity of the blade 34 as a whole against bending loads received from the sides of the blade 34, even if the thickness of each segmented blade 51 is reduced.

[0058] Specifically, as shown in Figure 4, the following three loads act on the side surface of the blade 34. On the side surface 51s of the divided blade 51 closest to the compression chamber 31c, a load Fs1 acts on the portion protruding into the cylinder chamber 31, based on the pressure of the gaseous refrigerant compressed in the compression chamber 31c. At this time, the load F1 is received by the first support point P1 and the second support point P2 of the blade groove 37, and a load Fs2 acts on the side surface 51s of the divided blade 51 closest to the suction chamber 31s at the first support point P1, and a load F3 acts on the end of the side surface 51s of the divided blade 51 closest to the compression chamber 31c at the second support point P2. As a result, a bending moment acts on the blade 34. The blade 34 has the rigidity to withstand this bending moment by stacking multiple divided blades 51 in the circumferential direction of the cylinder chamber 31.

[0059] The second support point P2 moves in conjunction with the reciprocating motion of the blade 34.

[0060] Furthermore, it is preferable that each of the multiple segmented blades 51 be the same size.

[0061] Specifically, as shown in Figures 6(A) and 6(B), each segmented blade 51 has the same dimensions, with a thickness of t2, a height of H, and a length of L. Therefore, by standardizing the plate members used for the segmented blades 51, parts processing and management become easier, and assembly efficiency is improved.

[0062] The split blade 51 has a pair of notches 53 cut out on its back surface 51b. The blade spring 40 comes into contact with the pair of notches 53.

[0063] Figure 7 is a schematic enlarged view of region Q1 in Figure 2.

[0064] Furthermore, as shown in Figure 7, it is preferable that the compressor 2 satisfies the following relation (3) when the width of the blade groove 37 in the direction perpendicular to the radial direction is W (millimeters (mm)) and the thickness of the blade 34, that is, the thickness of substantially multiple segmented blades 51 stacked on top of each other, is T (millimeters (mm)). 0.01 mm < (width W) - (thickness T) < 0.03 mm (3)

[0065] When the above relation (3) is satisfied, a gap is secured between the blade groove 37 and the blade 34 including the split blade 51. This gap is the difference between the width W and the thickness T, and ensures an appropriate oil film on the side surface of the blade 34, that is, on the sliding surface between the side surface 51s of the split blade 51 and the blade groove 37. The oil film ensures the sliding properties between the split blade 51 and the blade groove 37, and also suppresses the flow of gaseous refrigerant from the back side of the blade 34 toward the tip side through this gap toward the suction chamber 31s side in the cylinder chamber 31. This improves the efficiency and reliability of the compression mechanism 13 and, consequently, the compressor 2.

[0066] Furthermore, among the multiple segmented blades 51, the distance between adjacent segmented blades 51 is less than 0.01 millimeters, and in some cases, this distance may be virtually nonexistent.

[0067] As described above, the compressor 2 and refrigeration cycle device 1 according to this embodiment include a blade 34 that includes a plurality of segmented blades 51 arranged adjacent to each other in the circumferential direction of the cylinder chamber 31. Each of the plurality of segmented blades 51 receives the high-pressure discharge pressure Pd of the gaseous refrigerant in the sealed container 11 in a distributed manner at its back surface 51b. This reduces the load on the plurality of segmented blades 51 that presses their respective front surfaces 51t from their respective back surfaces 51b against the outer circumferential surface 33a of the roller 33. Therefore, the compressor 2 and refrigeration cycle device 1 can suppress a decrease in lubricity when the front surfaces of the blades 34, that is, the front surfaces 51t of each segmented blade 51, come into contact with the outer circumferential surface 33a of the roller 33. Thus, the compressor 2 and refrigeration cycle device 1 can improve the reliability of the compressor 2 by suppressing abnormal wear of the front surfaces of the blades 34 and the outer circumferential surface 33a of the roller 33.

[0068] The compressor 2 and refrigeration cycle device 1 according to this embodiment are equipped with a blade 34 that includes a plurality of segmented blades 51 of the same size. Therefore, by standardizing the plate members used as segmented blades 51, the compressor 2 and refrigeration cycle device 1 facilitate parts processing and management, and improve assembly efficiency. In other words, the compressor 2 and refrigeration cycle device 1 can have superior manufacturability due to the standardization of the plate members used as segmented blades 51.

[0069] In this embodiment, the compressor 2 and refrigeration cycle device 1 satisfy the above relation (3) when the width of the blade groove 37 in a direction perpendicular to the radial direction is W and the thickness of the stacked divided blades 51 is T. This ensures an appropriate gap between the blade groove 37 and the blade 34 including the divided blades 51. This gap ensures an appropriate oil film on the sliding surfaces of the blade 34 and the blade groove 37. The oil film not only ensures sliding between the divided blades 51 and the blade groove 37, but also suppresses the flow of gaseous refrigerant from the back side to the front side of the blade 34 through this gap and into the suction chamber 31s side of the cylinder chamber 31. Therefore, the compressor 2 and refrigeration cycle device 1 can have excellent efficiency and reliability.

[0070] Therefore, the compressor 2 and refrigeration cycle device 1 according to this embodiment can suppress the decrease in lubricity between the tip surface of the blade 34 and the outer peripheral surface 33a of the roller 33, and thus have excellent reliability.

[0071] While several embodiments of the present invention have been described, these embodiments are presented as examples only and are not intended to limit the scope of the invention. These novel embodiments can be carried out in a variety of other forms, and various omissions, substitutions, and modifications can be made without departing from the spirit of the invention. These embodiments and their variations are included in the scope and spirit of the invention, as well as in the claims of the invention and its equivalents. [Explanation of Symbols]

[0072] 1...Refrigeration cycle unit, 2...Rotary compressor (compressor), 3...Radiator, 5...Expansion device, 6...Heat absorber, 7...Accumulator, 7a...Suction pipe, 8...Refrigerant piping, 8a...Discharge pipe, 11...Sealed container, 11a...Body, 11b...Upper end plate, 11c...Lower end plate, 12...Electric motor, 13...Compression mechanism, 15...Crankshaft, 15a...Intermediate section, 15b...Lower end section, 16...Main bearing, 17...Sub-bearing, 21...Stator, 22...Rotor, 23...Stator core, 23a, 23b...End face, 24A, 24B...Insulating end plate, 2 5...Rotor core, 26...Eccentric section, 31...Cylinder chamber, 31c...Compression chamber, 31s...Suction chamber, 32...Cylinder, 33...Roller, 33a...Outer surface, 34, 34C...Blade, 34Cb...Back surface, 34Ct...Tip surface, 35...Suction port, 36...Discharge port, 37...Blade groove, 39...Blade back pressure chamber, 40...Blade spring, 41...Fastening member, 42...Discharge valve mechanism, 43...Discharge muffler, 51...Split blade, 51b...Back surface, 51s...Side surface, 51t...Tip surface, 53...Notch.

Claims

1. A sealed container, A compression mechanism disposed within the sealed container and capable of compressing the refrigerant, An electric motor is placed inside the sealed container to drive the compression mechanism, A crankshaft having an eccentric portion that is eccentric from the rotational centerline, which transmits the rotational driving force of the electric motor to the compression mechanism, The compression mechanism is A cylinder having a circular cylinder chamber inside, A roller that is fitted onto the eccentric portion and positioned in the cylinder chamber, The system includes a blade that contacts the roller and divides the cylinder chamber into a suction chamber and a compression chamber, The compressor includes a plurality of segmented blades arranged adjacent to each other in the circumferential direction of the cylinder chamber.

2. The compressor according to claim 1, wherein each of the plurality of segmented blades is the same size.

3. The cylinder has a blade groove that extends radially in the cylinder chamber and in which the blade is arranged, The compressor according to claim 1, wherein the following relational expression (3) is satisfied when the width of the blade groove in a direction perpendicular to the radial direction is W (millimeters) and the thickness of the multiple divided blades stacked together is T (millimeters). 0.01 mm < W-T < 0.03 mm (3)

4. The compressor according to claim 1, Heat sink and Expansion device and Heat absorber and A refrigeration cycle device comprising a compressor, a heat exchanger, an expansion device, and a heat absorber, and refrigerant piping for circulating the refrigerant.

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