Rotary compressor

Abstract

The present invention provides a rotary compressor that can suppress over-compression of compressed refrigerant compressed in a compression chamber and has excellent energy saving and reliability. The rotary compressor (1) comprises: a discharge hole (190) provided on an end plate (160) and partially located outside an inner wall (123) of a cylinder body; and a discharge groove (137) provided on an inner wall (123) of the cylinder body and connected to the compression chamber (133) and the discharge hole (190). The compression chamber (133) shrinks with the revolution of an annular piston (125) to compress the refrigerant, wherein the discharge hole (190) faces an end (128a) of the inner wall (123) of the cylinder body on the compression chamber side of the vane groove (128).

Description

Technical Field

[0001] The present invention relates to a rotary compressor used in a refrigeration cycle of an air conditioner device. Background Art

[0002] Figure 7 FIG. 2 is an enlarged cross-sectional view showing the first and second compression parts of a conventional rotary compressor. Figure 7 As shown, the existing rotary compressor has a compression part 12, which includes: an annular cylinder 121S, 121T, which has suction holes (not shown) and blade grooves 128S, 128T radially arranged on the side; an end plate (not shown), which closes the end of the cylinder 121S, 121T; annular pistons 125S, 125T, which are engaged with eccentric parts 152S, 152T (not shown) of a rotating shaft driven by a motor, and revolve in the cylinder 121S, 121T along the cylinder inner wall 123S, 123T of the cylinder 121S, 121T, and form working chambers 130S, 130T between the cylinder inner wall 123S, 123T; and blades 127S, 127T, which are arranged on the cylinder 121S The vane grooves 128S and 128T of the cylinder bodies 121S and 121T protrude into the working chambers 130S and 130T and abut against the annular pistons 125S and 125T, thereby dividing the working chambers 130S and 130T into suction chambers 131S and 131T and compression chambers 133S and 133T. Discharge holes 190S and 190T for discharging the compressed refrigerant in the compression chambers 133S and 133T to the outside of the compression chambers 133S and 133T are provided near the vane grooves 128S and 128T of the cylinder bodies 121S and 121T. Notches (discharge grooves) 137S and 137T for guiding the compressed refrigerant in the compression chambers 133S and 133T to the discharge holes 190S and 190T are provided near the vane grooves 128S and 128T of the cylinder bodies 121S and 121T.

[0003] One side of the edge of the cutout formed by the inner circumferential surface of the cutout 137S, 137T and the inner wall surface of the cylinder body on the compression chamber side is arranged to be located at the corner formed by the inner circumferential surface of the blade groove 128S, 128T and the inner wall surface of the cylinder body on the compression chamber side. That is, one side of the edge of the cutout formed by the inner circumferential surface of the cutout 137S, 137T and the surface of the cylinder body wall 123S, 123T is arranged to overlap with the corner formed by the inner circumferential surface of the blade groove 128S, 128T and the surface of the cylinder body wall 123S, 123T. Therefore, the first and second annular pistons 125S and 125T revolve counterclockwise, and the contact points between the first and second annular pistons 125S and 125T and the first and second cylinder body inner walls 123S and 123T are close to the first and second vane grooves 128S and 128T. After the first and second annular pistons 125S and 125T completely block the first and second discharge holes 190S and 190T, the cutouts 137S and 137T also connect the first and second small spaces 138S and 138T of the first and second compression chambers 133S and 133T with the first and second discharge holes 190S and 190T, so that the compressed refrigerant gas in the first and second small spaces 138S and 138T is released to the first and second discharge holes 190S and 190T, which can prevent over-compression of the refrigerant, reduce over-compression loss, and improve compression efficiency.

[0004] Prior Art Literature

[0005] Patent Literature

[0006] Patent Document 1: Japanese Patent Application Publication No. 2014-88836 Summary of the invention

[0007] Problems to be solved by the invention

[0008] However, in the prior art shown in Patent Document 1, one side of the edge of the cutout portion formed by the inner circumferential surface of the cutout portion 137S, 137T and the surface of the cylinder inner wall 123S, 123T is designed to overlap with the corner formed by the inner circumferential surface of the blade groove 128S, 128T and the surface of the cylinder inner wall 123S, 123T. However, in manufacturing, when one side of the edge of the cutout portion deviates from the corner, the first and second small spaces 138S, 138T will remain near the top dead center of the first and second annular pistons 125S, 125T, resulting in a problem that over-compression of the refrigerant cannot be completely prevented.

[0009] In addition, when one side of the edge of the cutout portion 137S, 137T overlaps with the position of the corner formed by the inner circumferential surface of the blade groove 128S, 128T and the inner wall surface of the cylinder body on the compression chamber side, since the wall portion formed by the inner circumferential surface of the blade groove 128S, 128T and the inner circumferential surface of the cutout portion 137S, 137T is formed at an acute angle, there is also a reliability problem that the wall portion formed at an acute angle is easily damaged.

[0010] In view of the above-mentioned problems, the first object of the present invention is to prevent over-compression of refrigerant, reduce over-compression loss, and improve compression efficiency. The second object of the present invention is to provide a rotary compressor with excellent reliability, in which the wall portion formed by the inner wall surface of the blade groove 128S, 128T and the inner peripheral wall surface of the cut-out portion 137S, 137T does not form an acute angle.

[0011] Means for solving problems

[0012] One embodiment of the present invention is a rotary compressor, which comprises: an annular cylinder body, which is provided with a suction hole and a blade groove; an end plate, which closes the end of the cylinder body; a discharge hole, which is provided on the end plate and is partially located on the outer side of the cylinder inner wall of the cylinder body; an annular piston, which is engaged with an eccentric portion of a rotating shaft driven by a motor, revolves in the cylinder body along the inner wall of the cylinder body, and forms a working chamber between the annular piston and the inner wall of the cylinder body; and a blade, which protrudes from the blade groove provided in the cylinder body into the working chamber and abuts against the annular piston, dividing the working chamber into a suction chamber connected to the suction hole and a compression chamber connected to the discharge hole, the compression chamber shrinking as the annular piston revolves, thereby compressing the refrigerant, wherein the discharge hole faces a corner formed by the inner wall of the blade groove and the inner wall of the cylinder body on the compression chamber side.

[0013] Another embodiment of the present invention is a rotary compressor, in which in one embodiment of the rotary compressor, a discharge groove connected to the compression chamber and the discharge hole is formed on the inner wall of the cylinder body on the compression chamber side, and the two side edges of the discharge groove formed by the inner circumferential wall of the discharge groove and the inner wall of the cylinder body are separated from the corner formed by the inner wall of the blade groove and the inner wall of the cylinder body on the compression chamber side.

[0014] Effects of the Invention

[0015] According to one embodiment of a rotary compressor, the discharge hole faces a corner formed by the inner wall of the vane groove and the inner wall of the cylinder body on the compression chamber side, so the compression chamber formed between the inner wall of the cylinder body and the annular piston is connected to the discharge hole before the annular piston reaches the top dead center. Therefore, the compressed refrigerant compressed in the compression chamber will not remain, and over-compression of the refrigerant can be suppressed.

[0016] According to another embodiment of a rotary compressor, the two side edges of the discharge groove formed by the inner circumferential wall of the discharge groove and the inner wall of the cylinder body are separated from the corner formed by the inner wall of the blade groove and the inner wall of the cylinder body on the compression chamber side, thereby preventing the wall portion formed by the inner wall surface of the blade groove and the inner circumferential wall surface of the cutout portion from being easily damaged. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 It is a longitudinal sectional view of the rotary compressor involved in the present invention.

[0018] Figure 2 It is a top view showing the compression part of the rotary compressor involved in the present invention.

[0019] Figure 3 This is an enlarged top view of the compression portion of Example 1.

[0020] Figure 4 It is along Figure 3 Cross-sectional view of line A-A.

[0021] Figure 5 It is an enlarged plan view showing the compression portion just before the top dead center.

[0022] Figure 6 This is an enlarged plan view showing the compression portion of Example 2.

[0023] Figure 7 It is a top view showing the compression part of a conventional rotary compressor.

[0024] Figure 8 This is a diagram showing the relationship between the ratio C / V of the inlet area C of the discharge hole to the discharge volume V of the cylinder chamber of the compression part and the efficiency in Example 1.

[0025] Fig. 9 This is a diagram showing the relationship between the seal width B of the blade and the efficiency in Example 1. DETAILED DESCRIPTION

[0026] Hereinafter, an embodiment of the rotary compressor according to the present invention will be described in detail based on the drawings. However, the present invention is not limited to the embodiment.

[0027] Example 1

[0028] Figure 1 is a longitudinal sectional view showing an embodiment of a rotary compressor according to the present invention, Figure 2 It is a top view showing the first and second compression parts of Example 1.

[0029] like Figure 1As shown, the rotary compressor 1 of the embodiment includes: a compression unit 12 arranged at the lower part of a closed vertically cylindrical compressor frame 10; and a motor 11 arranged at the upper part of the compressor frame 10 to drive the compression unit 12 via a rotating shaft 15.

[0030] The stator 111 of the motor 11 is formed in a cylindrical shape and is shrink-fitted to the inner peripheral surface of the compressor frame 10. The rotor 112 of the motor 11 is arranged inside the cylindrical stator 111 and is shrink-fitted to the rotating shaft 15 that mechanically connects the motor 11 and the compressor 12.

[0031] The compression section 12 includes: a first compression section 12S; and a second compression section 12T, which is arranged in parallel with the first compression section 12S and stacked on the upper side of the first compression section 12S. Figure 2 As shown, the first compression section 12S and the second compression section 12T include an annular first cylinder 121S and a second cylinder 121T having first suction holes 135S, second suction holes 135T, first blade grooves 128S, and second blade grooves 128T radially arranged in the first lateral extension 122S and the second lateral extension 122T.

[0032] like Figure 2 As shown, the first cylinder body 121S and the second cylinder body 121T have circular first cylinder inner walls 123S and second cylinder inner walls 123T formed concentrically with the rotating shaft 15 of the motor 11. The first annular piston 125S and the second annular piston 125T having an outer diameter smaller than the inner diameter of the cylinder body are respectively arranged in the first cylinder inner wall 123S and the second cylinder inner wall 123T, and the first working chamber 130S and the second working chamber 130T for sucking, compressing and discharging refrigerant gas are formed between the first cylinder inner wall (inner peripheral surface) 123S and the second cylinder inner wall (inner peripheral surface) 123T and the outer peripheral surface 125Sa of the first annular piston 125S and the outer peripheral surface 125Ta of the second annular piston 125T.

[0033] The first and second cylinder bodies 121S and 121T are provided with first and second blade grooves 128S and 128T extending over the entire height of the cylinder bodies in the radial direction from the first and second cylinder inner walls 123S and 123T, and the first and second blades 127S and 127T are respectively slidably fitted in the first and second blade grooves 128S and 128T in the form of flat plates. The cross-section of the first and second blades 127S and 127T cut at a plane perpendicular to the rotation axis, i.e., the end face of the blade is an elongated rectangle consisting of a short side and a long side, and hereinafter, the width of the short side of the end face of the blade is referred to as the width of the end face of the first and second blades 127S and 127T.

[0034] like Figure 2As shown, first spring holes 124S and second spring holes 124T are formed in the inner part of the first vane groove 128S and the second vane groove 128T so as to communicate with the outer periphery of the first cylinder 121S and the second cylinder 121T. A vane spring (not shown) is inserted into the first spring hole 124S and the second spring hole 124T to press the back of the first vane 127S and the second vane 127T. When the rotary compressor 1 is started, the reaction force of the blade spring causes the first blade 127S and the second blade 127T to protrude from the first blade groove 128S and the second blade groove 128T into the first working room 130S and the second working room 130T, and their front ends abut against the outer peripheral surfaces of the first annular piston 125S and the second annular piston 125T. Through the first blade 127S and the second blade 127T, the first working room 130S and the second working room 130T are divided into a first suction chamber 131S and a second suction chamber 131T and a first compression chamber 133S and a second compression chamber 133T.

[0035] Furthermore, a first pressure introduction passage 129S and a second pressure introduction passage 129T are formed in the first cylinder 121S and the second cylinder 121T. The first pressure introduction passage 129S and the second pressure introduction passage 129T pass through Figure 1 The opening R shown connects the inner part of the first vane groove 128S and the second vane groove 128T with the compressor frame 10 to introduce the compressed refrigerant gas in the compressor frame 10, and applies back pressure to the first vane 127S and the second vane 127T by the pressure of the refrigerant gas.

[0036] The first cylinder 121S and the second cylinder 121T are provided with a first suction hole 135S and a second suction hole 135T for communicating the first suction chamber 131S and the second suction chamber 131T with the outside so that refrigerant can be sucked into the first suction chamber 131S and the second suction chamber 131T from the outside.

[0037] In addition, if Figure 1 As shown, between the first cylinder 121S and the second cylinder 121T, an intermediate partition 140 is arranged to divide and seal the first working chamber 130S of the first cylinder 121S and the second working chamber 130T of the second cylinder 121T. At the lower end of the first cylinder 121S, a lower end plate 160S is arranged to seal the first working chamber 130S of the first cylinder 121S. In addition, at the upper end of the second cylinder 121T, an upper end plate 160T is arranged to seal the second working chamber 130T of the second cylinder 121T.

[0038] The lower end plate 160S is formed with an auxiliary bearing 161S, which rotatably supports the auxiliary shaft 151 of the rotating shaft 15. The upper end plate 160T is formed with a main bearing 161T, which rotatably supports the main shaft 153 of the rotating shaft 15.

[0039] The rotating shaft 15 includes a first eccentric portion 152S and a second eccentric portion 152T which are eccentric and are shifted in phase by 180 degrees from each other. The first eccentric portion 152S is rotatably fitted in the first annular piston 125S of the first compression portion 12S, and the second eccentric portion 152T is rotatably fitted in the second annular piston 125T of the second compression portion 12T.

[0040] When the rotating shaft 15 rotates, the first annular piston 125S and the second annular piston 125T move inwardly in the first cylinder 121S and the second cylinder 121T along the inner wall 123S and the inner wall 123T of the first cylinder. Figure 2 The first vane 127S and the second vane 127T reciprocate in counterclockwise revolution. The first annular piston 125S, the second annular piston 125T and the first vane 127S and the second vane 127T move in a reciprocating motion. The volumes of the first suction chamber 131S, the second suction chamber 131T and the first compression chamber 133S and the second compression chamber 133T change continuously through the movement of the first annular piston 125S, the second annular piston 125T and the first vane 127S and the second vane 127T, and the compression section 12 continuously inhales, compresses and discharges the refrigerant gas. The characteristic structure of the compression section 12 will be described later.

[0041] like Figure 1 As shown in FIG. 1 , a lower muffler cover 170S is disposed on the lower side of the lower end plate 160S, and a lower muffler chamber 180S is formed between the lower end plate 160S and the lower end plate 160S. In addition, the first compression section 12S opens to the lower muffler chamber 180S. That is, a first discharge hole 190S (see FIG. 1 ) is provided near the first vane 127S of the lower end plate 160S, which connects the first compression chamber 133S of the first cylinder 121S with the lower muffler chamber 180S. Figure 2 ), a first discharge valve 200S of a reed valve type is disposed in the first discharge port 190S to prevent the backflow of the compressed refrigerant gas.

[0042] The lower muffler chamber 180S is an annular chamber that allows the discharge side of the first compression unit 12S to pass through the refrigerant passage 136 (see Figure 2) and a part of the communication passage connected to the upper muffler chamber 180T. The lower muffler chamber 180S reduces the pressure pulsation of the discharged refrigerant gas. In addition, the first discharge valve pressing member 201S overlapping with the first discharge valve 200S and used to limit the deflection valve opening amount of the first discharge valve 200S is fixed together with the first discharge valve 200S by rivets. The first discharge hole 190S, the first discharge valve 200S and the first discharge valve pressing member 201S constitute the first discharge valve portion of the lower end plate 160S.

[0043] like Figure 1 As shown, an upper muffler cover 170T is arranged on the upper side of the upper end plate 160T, and an upper muffler chamber 180T is formed between the upper end plate 160T and the upper end plate 160T. A second discharge hole 190T (see FIG. 1 ) is provided near the second vane 127T of the upper end plate 160T, which connects the second compression chamber 133T of the second cylinder 121T with the upper muffler chamber 180T. Figure 2 ), a reed valve type second discharge valve 200T is arranged in the second discharge hole 190T to prevent the backflow of the compressed refrigerant gas. In addition, a second discharge valve pressing member 201T overlaps with the second discharge valve 200T and is used to limit the deflection valve opening amount of the second discharge valve 200T and is fixed together with the second discharge valve 200T by rivets. The upper muffler chamber 180T reduces the pressure pulsation of the discharged refrigerant. The second discharge hole 190T, the second discharge valve 200T and the second discharge valve pressing member 201T constitute the second discharge valve portion of the upper end plate 160T.

[0044] The first cylinder block 121S, the lower end plate 160S, the lower muffler cover 170S, the second cylinder block 121T, the upper end plate 160T, the upper muffler cover 170T and the middle partition plate 140 are fastened together by a plurality of through bolts 175, etc. In the compression part 12 fastened together by the through bolts 175, etc., the outer periphery of the upper end plate 160T is fixed to the compressor frame 10 by spot welding, and the compression part 12 is fixed to the compressor frame 10.

[0045] The outer peripheral wall of the cylindrical compressor frame 10 is provided with a first through hole 101 and a second through hole 102 in order to allow the first suction pipe 104 and the second suction pipe 105 to pass through in the axial direction. In addition, on the outer side of the compressor frame 10, a liquid reservoir 25 consisting of an independent cylindrical sealed container is held by a liquid reservoir bracket 252 and a liquid reservoir belt 253.

[0046] At the top center of the liquid reservoir 25, a system connecting pipe 255 connected to the evaporator of the refrigeration cycle is connected, and to the bottom through hole 257 arranged at the bottom of the liquid reservoir 25, a first low-pressure connecting pipe 31S and a second low-pressure connecting pipe 31T are connected, each of which has one end extending to the upper part of the interior of the liquid reservoir 25 and the other end connected to the other end of the first suction pipe 104 and the second suction pipe 105.

[0047] The first low-pressure communication pipe 31S and the second low-pressure communication pipe 31T that guide the low-pressure refrigerant of the refrigeration cycle to the first compression part 12S and the second compression part 12T via the accumulator 25 are connected to the first suction hole 135S and the second suction hole 135T of the first cylinder 121S and the second cylinder 121T via the first suction pipe 104 and the second suction pipe 105 as the suction part (see Figure 2 That is, the first suction hole 135S and the second suction hole 135T are connected in parallel with the evaporator of the refrigeration cycle.

[0048] A discharge pipe 107 as a discharge portion connected to the refrigeration cycle and discharging high-pressure refrigerant gas to the condenser side of the refrigeration cycle is connected to the top of the compressor housing 10. That is, the first discharge hole 190S and the second discharge hole 190T are connected to the condenser of the refrigeration cycle.

[0049] Lubricating oil is sealed in the compressor frame 10 to a height substantially up to the second cylinder 121T. The lubricating oil is sucked up from an oil supply pipe 16 mounted on the lower end of the rotating shaft 15 by a vane pump (not shown) inserted in the lower portion of the rotating shaft 15, circulated in the compression section 12, lubricated the sliding parts, and sealed the minute gaps in the compression section 12.

[0050] Next, refer to Figure 3 to Figure 5 , the characteristic structure of the rotary compressor 1 of Example 1 is described. Figure 3 yes Figure 2 An enlarged top view of the compression portion shown, Figure 4 It is along Figure 3 The cross-sectional view of the A-A line, Figure 5 It is an enlarged top view of the compression part when the annular piston is located near the top dead center. In addition, in the following description, regarding the content of the common structure such as the first annular piston 125S and the second annular piston 125T, the description of the "first" and "second" in the name, the suffix "S" and "T" of the symbol is sometimes omitted, and repeated description is omitted.

[0051] A first discharge hole 190S and a second discharge hole 190T are provided on the first compression chamber 133S and the second compression chamber 133T side of the lower end plate 160S and the upper end plate 160T, which are communicated with the first compression chamber 133S and the second compression chamber 133T. A portion of the first discharge hole 190S and the second discharge hole 190T is located outside the first cylinder inner wall 123S and the second cylinder inner wall 123T, and is arranged at a position facing the first corner 128Sa and the second corner 128Ta formed by the first vane groove inner wall 128Sb of the first vane groove 128S, the second vane groove inner wall 128Tb of the second vane groove 128T and the first cylinder inner wall 123S and the second cylinder inner wall 123T on the compression chamber side (hereinafter referred to as the first corner 128Sa and the second corner 128Ta of the cylinder inner wall on the compression chamber side of the vane groove). That is, when viewed from the axial direction of the rotating shaft 15, the first discharge hole 190S and the second discharge hole 190T are arranged so that the first corner 128Sa of the compression chamber side cylinder inner wall of the vane groove and the second corner 128Ta of the compression chamber side cylinder inner wall of the vane groove enter therein.

[0052] On the first compression chamber 133S side and the second compression chamber 133T side, the first cylinder body 121S and the second cylinder body 121T have first discharge grooves 137S and second discharge grooves 137T opened on the first cylinder inner wall 123S and the second cylinder inner wall 123T and the end faces of the first cylinder body 121S and the second cylinder body 121T. The first discharge grooves 137S and the second discharge grooves 137T connect the first compression chamber 133S and the second compression chamber 133T with the first discharge hole 190S and the second discharge hole 190T. The first discharge groove 137S and the second discharge groove 137T, which are formed by the inner peripheral walls of the first discharge groove 137S and the second discharge groove 137T and the cylinder inner wall 123S and the cylinder inner wall 123T on the first compression chamber side, are arranged at a position separated from the first corner 128Sa and the second corner 128Ta of the cylinder inner wall on the compression chamber side of the blade groove.

[0053] The openings of the first discharge groove 137S and the second discharge groove 137T formed on the end faces of the first cylinder 121S and the second cylinder 121T are arc-shaped, and have a curvature radius R2 that is equal to or similar to the radius R1 of the first discharge hole 190S and the second discharge hole 190T (for example, 0.9R1≤R2≤1.1R1), and are formed into a semicircular shape (or a semiconical shape) that is inclined from the end faces of the first cylinder 121S and the second cylinder 121T toward the first cylinder inner wall 123S and the second cylinder inner wall 123T in a manner that the depth from the openings formed on the end faces of the first cylinder 121S and the second cylinder 121T becomes shallower as it moves toward the inner side. Figure 4As shown, the first discharge groove 137S and the second discharge groove 137T are formed only in the portion of the first cylinder inner wall 123S and the second cylinder inner wall 123T close to the lower end plate 160S and the upper end plate 160T. This is because if the first discharge groove 137S and the second discharge groove 137T are formed over the entire area of ​​the first cylinder inner wall 123S and the second cylinder inner wall 123T in the up-down direction, the mechanical strength of the first cylinder 121S and the second cylinder 121T is reduced, and the compressed refrigerant gas remaining in the first discharge groove 137S and the second discharge groove 137T flows back to the first compression chamber 133S and the second compression chamber 133T, and the volumetric efficiency of the refrigerant compression is reduced.

[0054] like Figure 5 As shown, in the rotary compressor 1 of Example 1, the first discharge hole 190S and the second discharge hole 190T are arranged at the first corner 128Sa and the second corner 128Ta of the inner wall of the cylinder body on the compression chamber side facing the vane groove. Therefore, before the first annular piston 125S and the second annular piston 125T revolve counterclockwise and reach the top dead center, the first small space 138S and the second small space 138T (which are surrounded by the first cylinder inner wall 123S, the second cylinder inner wall 123T and the first outer peripheral surface 125Sa, the second outer peripheral surface 125Ta of the first annular piston 125S, the second annular piston 125T and the first vane 127S, the second vane 127T) are formed. Figure 5 The hatched portion in the figure is connected to the first discharge hole 190S and the second discharge hole 190T. Therefore, the compressed refrigerant gas in the first small space 138S and the second small space 138T is discharged to the first discharge hole 190S and the second discharge hole 190T, thereby preventing over-compression of the refrigerant, reducing over-compression loss, and improving compression efficiency.

[0055] Furthermore, in the rotary compressor 1 of Example 1, the first edge 128Sc and the second edge 128Tc on both sides of the first discharge groove 137S and the second discharge groove 137T formed by the inner circumferential wall of the first discharge groove 137S and the second discharge groove 137T and the cylinder inner wall 123S and 123T on the compression chamber side are arranged at a position separated from the first corner 128Sa and the second corner 128Ta of the cylinder inner wall on the compression chamber side of the blade groove, so that the wall portion formed by the first blade groove inner wall 128Sb, the second blade groove inner wall 128Tb and the inner circumferential surface of the first discharge groove 137S and the second discharge groove 137T will not form an acute angle, thereby being able to prevent the end portions from being easily damaged.

[0056] Next, based on Figure 3 and Figure 8 The inlet area C (mm) of the first and second discharge holes 190 is shown in FIG. 2 ) relative to the displacement volume V (mm) of the cylinder 121 3) ratio C / V and the efficiency E of the rotary compressor 1.

[0057] The inlet area C of the discharge hole 190 is Figure 3 The inlet area C is the sum of the area D of the portion of the discharge hole 190 that does not overlap with the blade 127 and the end surface of the cylinder body 121 and is exposed to the end plate 160 and the area E of the portion that overlaps the discharge hole 190 and the discharge groove 137. The inlet area C is the actual area of ​​the discharge hole 190 through which the compressed refrigerant flows. Figure 8 It can be seen from the experiment that the efficiency E is improved by setting 3.0≤C / V≤4.5.

[0058] Next, based on Figure 3 and Fig. 9 The relationship between the sealing width B between the discharge hole 190 and the blade 127 (the width of the end surface of the blade 127 ) and the efficiency E of the rotary compressor 1 will be described.

[0059] The sealing width B between the discharge hole 190 and the blade 127 is Figure 3 The width of the blade 127 is shown as the width of the blade 127 minus the portion where the discharge hole 190 overlaps with the blade 127. Fig. 9 It can be seen from the experiment that the efficiency E is improved by setting 2.2 (mm) ≤ B.

[0060] In the first embodiment, the first discharge groove 137S and the second discharge groove 137T are provided on the first cylinder inner wall 123S and the second cylinder inner wall 123T to communicate the first compression chamber 133S and the second compression chamber 133T with the first discharge hole 190S and the second discharge hole 190T, but they are not necessarily provided. However, in order to sufficiently ensure that the inlet area of ​​the first discharge hole 190S and the second discharge hole 190T is effective, it is preferable to provide the first discharge groove 137S and the second discharge groove 137T.

[0061] Example 2

[0062] Next, refer to Figure 6 , the characteristic structure of the rotary compressor 1 of Example 2 is described. In addition, the same symbols are marked on the same structure as that of Example 1, and the detailed description is omitted. Figure 6 This is an enlarged cross-sectional view showing the first and second compression parts of Example 2.

[0063] like Figure 6As shown, near the first blade groove 128S and the second blade groove 128T on the first compression chamber 133S and the second compression chamber 133T side of the lower end plate 160S and the upper end plate 160T, a portion is located on the outside of the inner wall 123S of the first cylinder body and the inner wall 123T of the second cylinder body, and the first discharge hole 190S and the second discharge hole 190T connected to the first compression chamber 133S and the second compression chamber 133T are set not to overlap with the first blade 127S and the second blade 127T.

[0064] In addition, the first cylinder 121S and the second cylinder 121T on the first compression chamber 133S side and the second compression chamber 133T side are formed with a first discharge groove 237S and a second discharge groove 237T which are open on the first cylinder inner wall 123S and the second cylinder inner wall 123T and the end surface of the first cylinder 121S and the second cylinder 121T, and the first discharge groove 237S and the second discharge groove 237T connect the first compression chamber 133S and the second compression chamber 133T with the first discharge hole 190S and the second discharge hole 190T. In addition, the first discharge groove 237S and the second discharge groove 237T are also open on the first vane groove inner wall 128Sb and the second vane groove inner wall 128Tb on the first compression chamber 133S side and the second compression chamber 133T side.

[0065] The openings of the first discharge groove 237S and the second discharge groove 237T formed on the end surfaces of the first cylinder body 121S and the second cylinder body 121T are arc-shaped, and have a curvature radius larger than the radius R1 of the first discharge hole 190S and the second discharge hole 190T. As the depth from the first cylinder inner wall 123S and the second cylinder inner wall 123T becomes shallower from the openings formed on the end surfaces of the first cylinder body 121S and the second cylinder body 121T toward the inner wall 123S and the second cylinder inner wall 123T, they are formed into a semicircular shape (or a semiconical shape) inclined from the end surfaces of the first cylinder body 121S and the second cylinder body 121T toward the inner wall 123S and the second cylinder inner wall 123T. Furthermore, the angle of the edge formed by the inner peripheral walls of the first discharge groove 237S and the second discharge groove 237T intersecting with the first blade groove inner walls 128Sb and the second blade groove inner walls 128Tb of the first blade groove 128S and the second blade groove 128T is substantially a right angle or an angle larger than a right angle.

[0066] In the rotary compressor 1 of Example 2, the first annular piston 125S and the second annular piston 125T revolve counterclockwise, and the contact points of the first annular piston 125S and the second annular piston 125T with the inner wall 123S of the first cylinder body and the inner wall 123T of the second cylinder body are close to the first vane groove 128S and the second vane groove 128T. After the first annular piston 125S and the second annular piston 125T completely block the first discharge hole 190S and the second discharge hole 190T, the first discharge groove 237S and the second discharge groove 237T also make the first small space 138S and the second small space 138T of the first compression chamber 133S and the second compression chamber 133T (refer to Figure 7 ) is connected to the first discharge hole 190S and the second discharge hole 190T, so that the compressed refrigerant gas in the first small space 138S and the second small space 138T is released to the first discharge hole 190S and the second discharge hole 190T, thereby preventing over-compression of the refrigerant, reducing over-compression loss, and improving compression efficiency.

[0067] In addition, in the rotary compressor 1 of Example 2, the angle of the edge formed by the inner circumferential wall of the first discharge groove 237S and the second discharge groove 237T intersecting with the first blade groove inner wall 128Sb and the second blade groove inner wall 128Tb of the first blade groove 128S and the second blade groove 128T is approximately a right angle or an angle larger than a right angle, so the wall portion formed by the first blade groove inner wall 128Sb, the second blade groove inner wall 128Tb and the inner circumferential surface of the first discharge groove 237S and the second discharge groove 237T will not form an acute angle, thereby preventing the end portion from being easily damaged.

[0068] In addition, in Embodiments 1 and 2, the embodiments of the two-cylinder type rotary compressor are described, but the rotary compressor of this embodiment can also be applied to a single-cylinder type rotary compressor and a two-stage compression type rotary compressor.

[0069] Explanation of symbols

[0070] 1... Rotary compressor, 10... Compressor frame (sealed container), 11... Motor, 12S, T... Compression section, 15... Rotating shaft, 121S, T... Cylinder, 123S, T... Cylinder inner wall, 125S, T... Annular piston, 125Sa, Ta... Outer peripheral surface of annular piston, 127S, T... Vane, 127Sw, Tw... Vane end surface, 128S, T... Vane groove, 128Sa, Ta... Compression chamber side wall of vane groove The end of the part, 128Sb, Tb...inner wall of the blade groove, 128Sc, Tc...edge of the blade groove, 130S, T...working room, 131S, T...suction chamber, 133S, T...compression chamber, 135S, T...suction hole, 137S, T...discharge groove, 138S, T...small space, 152S, T...eccentric part, 160S, T...end plate, 167S, T...gap, 190S, T...discharge hole, 237S, T...discharge groove.

Claims

1. A rotary compressor, characterized in that: have: An annular cylinder body is provided with a suction hole and a blade groove; an end plate that closes the end of the cylinder; A discharge hole is provided on the end plate and a portion of which is located outside the inner wall of the cylinder body; An annular piston is engaged with an eccentric portion of a rotating shaft driven by a motor, revolves along the inner wall of the cylinder, and forms a working chamber between the piston and the inner wall of the cylinder; a vane protruding from the vane groove provided in the cylinder body into the working chamber and abutting against the annular piston, so as to divide the working chamber into a suction chamber communicating with the suction hole and a compression chamber communicating with the discharge hole; as well as a discharge groove formed on the inner wall of the cylinder body of the compression chamber and communicating with the compression chamber and the discharge hole, The compression chamber shrinks as the annular piston revolves, thereby compressing the refrigerant. The discharge hole faces a corner formed by the inner wall of the vane groove and the inner wall of the cylinder body of the compression chamber. The two side edges of the discharge groove formed by the inner circumferential wall of the discharge groove and the inner wall of the cylinder body are separated from the corner formed by the inner wall of the vane groove and the inner wall of the cylinder body of the compression chamber, and a portion of the discharge groove is exposed in a direction opposite to the revolution direction of the annular piston in the circumferential direction of the cylinder body compared to the discharge hole.

2. The rotary compressor according to claim 1, characterized in that: The width B of the portion of the end surface of the blade that does not overlap with the discharge hole satisfies the following relationship: 2.2(mm)≤B.

3. The rotary compressor according to claim 1 or 2, characterized in that: The inlet area C of the discharge hole and the displacement volume V of the cylinder body satisfy the following relationship: C = D + E; D = the area of ​​the discharge hole exposed on the end plate; E = the area of ​​the portion where the discharge hole and the discharge slot overlap; 3.0(mm -1 )≤C / V≤4.5(mm -1 )。

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