JP6102760B2 - Rotary compressor - Google Patents

Description

  The present invention relates to a rotary compressor used for an air conditioner, a refrigerator, and the like.

  Conventionally, an electric element having a rotary drive shaft in a sealed casing and a rotary compression element that is driven by the rotary drive shaft and compresses refrigerant gas are provided. The rotary compression element has a hole through which the rotary drive shaft passes. And a middle plate disposed perpendicular to the central axis of the rotary drive shaft, and a refrigerant gas compression chamber provided at a position sandwiching the middle plate from both sides in the central axis direction of the rotary drive shaft An injection pipe introduced from the outside of the hermetic casing and connected to the injection pipe, and the first and second cylinder chambers are connected to the middle plate. A refrigerant gas passage branched to communicate with each of the cylinder chambers is provided, and the refrigerant cycle is passed through the injection pipe and the refrigerant gas passage. It is possible to inject the refrigerant gas separated in the gas and liquid into the first and second cylinder chambers, and the rotary compression element extends along the inner wall of each of the first and second cylinder chambers. A first roller and a second roller that revolve in a state of being out of phase with each other as the rotation drive shaft rotates, and the opening of the refrigerant gas passage to the first cylinder chamber and the opening to the second cylinder chamber The first roller and the second roller are configured so that at least one of the first roller and the second cylinder chamber has an opening to the cylinder chamber and an opening to the second cylinder chamber, respectively, so as to maintain a state where at least one of them is closed. A rotary compressor is disclosed in which the position and size of the opening of the refrigerant gas passage are set so that the rotation angle of the rotary drive shaft that is simultaneously closed is at least 5 degrees or more (for example, a patent) Document reference 1).

Japanese Patent No. 3979407

  In the above conventional technique, the rotation angle of the rotation drive shaft is such that the first roller and the second roller simultaneously block the opening of the refrigerant gas passage to the first cylinder chamber and the opening of the second cylinder chamber, respectively, at least 5 degrees. As described above, the position and size of the opening of the refrigerant gas passage are set. For this reason, there is a problem that the area where the opening of the refrigerant gas passage can be arranged is limited and the diameter of the opening has to be reduced, which makes processing difficult. In addition, when the diameter of the opening is small, there is a problem that lubricating oil or refrigerant in the cylinder chamber may block the opening, and a necessary injection flow rate cannot be ensured.

  The present invention has been made in view of the above, and has a wide area in which refrigerant gas passage openings (hereinafter referred to as “injection holes”) can be arranged, and the diameter of the injection holes can be increased to facilitate processing. In addition, an object of the present invention is to obtain a rotary compressor that can secure a necessary injection flow rate.

  In order to solve the above-described problems and achieve the object, the present invention includes a vertically-placed cylindrical compressor housing that is provided with a refrigerant discharge portion at the top and a refrigerant suction portion at the bottom and is sealed, A lower upper end plate disposed at a lower portion of the compressor housing, having annular first and second cylinders, a bearing portion and a discharge valve portion, and closing the end portions of the first and second cylinders; An intermediate partition plate arranged between the first and second cylinders and partitioning between them, and the first and second cylinders of the first and second cylinders fitted to the first and second eccentric parts of the rotating shaft supported by the bearing part First and second annular pistons that revolve around the cylinder along the inner peripheral surface to form first and second working chambers between the cylinder inner peripheral surface and the first and second cylinders. The first and second vane grooves protrude from the first and second vane grooves into the first and second working chambers. First and second vanes contacting the second annular piston and dividing the first and second working chambers into first and second suction chambers and first and second compression chambers; First and second compressors for sucking refrigerant from the low-pressure side of the refrigeration cycle and discharging refrigerant from the discharge unit through the compressor housing, and the upper portion of the compressor housing, A rotary compressor having a motor for driving the compression section via the intermediate partition plate, a vertical injection hole communicating with the first and second working chambers, and a refrigerant communicating with the injection hole. A horizontal hole for fitting an injection pipe for injecting into the first and second working chambers is provided, and the diameter of the injection hole is set in a range from φ0.8 mm to φ1.4 mm, and the first and second An annular piston is the first and first The revolution angle range of the first and second annular pistons that revolve in the cylinder to open and close the injection hole and open the injection hole in both the first and second working chambers is greater than 0 ° and less than 6 °. It is characterized by the above.

  According to the present invention, it is possible to obtain a rotary compressor that has a wide arrangement area of injection holes, can increase the diameter of the injection holes, is easy to process, and can secure a necessary injection flow rate. There is an effect.

FIG. 1 is a longitudinal sectional view showing a rotary compressor to which the present invention is applied. FIG. 2 is a cross-sectional view seen from the top of the first and second compression portions. FIG. 3 is a partially enlarged longitudinal sectional view showing a compression portion of an embodiment of the rotary compressor according to the present invention. FIG. 4 is a plan view of the intermediate partition plate of the embodiment. FIG. 5 is a cross-sectional view showing a state in which the second annular piston of the second compression section has revolved 50 ° clockwise from the top dead center. FIG. 6 is a cross-sectional view showing a state in which the first annular piston of the first compression portion has revolved 50 ° clockwise from the bottom dead center. FIG. 7 is a cross-sectional view showing a state in which the second annular piston of the second compression section has revolved 215 ° clockwise from the top dead center. FIG. 8 is a cross-sectional view showing a state in which the first annular piston of the first compression portion has revolved 215 ° clockwise from the bottom dead center. FIG. 9 shows a state in which the second annular piston of the second compression portion revolves 215 ° clockwise from the top dead center, and the first annular piston of the first compression portion revolves 215 ° clockwise from the bottom dead center FIG. FIG. 10 is a cross-sectional view showing a state in which the second annular piston of the second compression portion has revolved 230 ° clockwise from the top dead center. FIG. 11 is a cross-sectional view showing a state in which the first annular piston of the first compression portion has revolved 230 ° clockwise from the bottom dead center. FIG. 12 is a view showing an opening / closing state of the injection hole accompanying the revolution of the first and second annular pistons in the first and second compression portions. FIG. 13 is a view showing an opening / closing state of the injection hole accompanying the revolution of the first and second annular pistons when the diameter of the injection hole of the medium-sized model is φ ₁ = 0.8 to 1.4 mm. FIG. 14 is a view showing an opening / closing state of the injection hole accompanying the revolution of the first and second annular pistons when the diameter of the injection hole of the small model is φ ₁ = 0.8 to 1.4 mm. FIG. 15 is a view showing an opening / closing state of the injection hole accompanying the revolution of the first and second annular pistons when the diameter of the injection hole of the large model is φ ₁ = 0.8 to 1.4 mm.

  Embodiments of a rotary compressor according to the present invention will be described below in detail with reference to the drawings. Note that the present invention is not limited to the embodiments.

  FIG. 1 is a longitudinal sectional view showing an embodiment of a rotary compressor according to the present invention, and FIG. 2 is a transverse sectional view seen from above the first and second compression portions of the embodiment.

  As shown in FIG. 1, the rotary compressor 1 according to the embodiment is disposed at a lower portion of a sealed vertical cylindrical compressor housing 10 and an upper portion of the compressor housing 10. And a motor 11 that drives the compression unit 12 via the rotary shaft 15.

  The stator 111 of the motor 11 is formed in a cylindrical shape, and is fixed by being shrink-fitted on the inner peripheral surface of the compressor housing 10. The rotor 112 of the motor 11 is disposed inside the cylindrical stator 111 and is fixed by being shrink-fitted to a rotating shaft 15 that mechanically connects the motor 11 and the compression unit 12.

  The compression unit 12 includes a first compression unit 12S and a second compression unit 12T that is arranged in parallel with the first compression unit 12S and stacked on the upper side of the first compression unit 12S. As shown in FIG. 2, the first and second compression parts 12S and 12T are arranged radially to the first and second side projecting parts 122S and 122T, and the first and second suction holes 135S and 135T and the first And annular first and second cylinders 121S and 121T provided with second vane grooves 128S and 128T.

  As shown in FIG. 2, circular first and second cylinder inner walls 123 </ b> S and 123 </ b> T are formed in the first and second cylinders 121 </ b> S and 121 </ b> T concentrically with the rotating shaft 15 of the motor 11. In the first and second cylinder inner walls 123S, 123T, first and second annular pistons 125S, 125T having an outer diameter smaller than the cylinder inner diameter are arranged, respectively, and the first and second cylinder inner walls 123S, 123T, Between the first and second annular pistons 125S and 125T, there are formed first and second working chambers 130S and 130T for sucking, compressing and discharging the refrigerant gas.

  The first and second cylinders 121S and 121T are formed with first and second vane grooves 128S and 128T extending in the radial direction from the first and second cylinder inner walls 123S and 123T over the entire cylinder height. Flat plate-like first and second vanes 127S and 127T are slidably fitted in the second vane grooves 128S and 128T, respectively.

  As shown in FIG. 2, the first and second vane grooves 128S and 128T are communicated with the first and second vane grooves 128S and 128T from the outer peripheral portions of the first and second cylinders 121S and 121T at the back of the first and second vane grooves 128S and 128T. First and second spring holes 124S and 124T are formed in the first and second spring holes 124S and 124T, respectively. First and second vane springs (not shown) that press the back surfaces of the first and second vanes 127S and 127T are inserted into the first and second spring holes 124S and 124T.

  When the rotary compressor 1 is started, the first and second vane 127S and 127T are moved from the inside of the first and second vane grooves 128S and 128T by the repulsive force of the first and second vane springs. The first and second working chambers 130S, 130T, projecting into the working chambers 130S, 130T, their tips abutting against the outer peripheral surfaces of the first and second annular pistons 125S, 125T, and the first and second vanes 127S, 127T. 130T is partitioned into first and second suction chambers 131S and 131T and first and second compression chambers 133S and 133T.

  In addition, the first and second cylinders 121S and 121T communicate with the inner portions of the first and second vane grooves 128S and 128T and the inside of the compressor housing 10 through the opening R shown in FIG. First and second pressure introduction paths 129S and 129T are formed in which the compressed refrigerant gas in the housing 10 is introduced and back pressure is applied to the first and second vanes 127S and 127T by the pressure of the refrigerant gas. .

  The first and second cylinders 121S and 121T have a first communication between the first and second suction chambers 131S and 131T and the outside in order to suck the refrigerant from the outside into the first and second suction chambers 131S and 131T. And second suction holes 135S and 135T are provided.

  Further, as shown in FIG. 1, an intermediate partition plate 140 is disposed between the first cylinder 121S and the second cylinder 121T, and the first working chamber 130S (see FIG. 2) of the first cylinder 121S and the second cylinder. The second working chamber 130T (see FIG. 2) of 121T is partitioned and closed. A lower end plate 160S is disposed at the lower end of the first cylinder 121S, and closes the first working chamber 130S of the first cylinder 121S. An upper end plate 160T is disposed at the upper end portion of the second cylinder 121T, and closes the second working chamber 130T of the second cylinder 121T.

  A sub-bearing portion 161S is formed on the lower end plate 160S, and the sub-shaft portion 151 of the rotary shaft 15 is rotatably supported by the sub-bearing portion 161S. A main bearing portion 161T is formed on the upper end plate 160T, and the main shaft portion 153 of the rotary shaft 15 is rotatably supported by the main bearing portion 161T.

  The rotating shaft 15 includes a first eccentric portion 152S and a second eccentric portion 152T that are eccentric with a phase difference of 180 ° from each other. The first eccentric portion 152S is connected to the first annular piston 125S of the first compression portion 12S. The second eccentric portion 152T is rotatably fitted to the second annular piston 125T of the second compression portion 12T.

  When the rotary shaft 15 rotates, the first and second annular pistons 125S and 125T revolve in the first and second cylinders 121S and 121T in the clockwise direction in FIG. 2 along the first and second cylinder inner walls 123S and 123T. Then, following this, the first and second vanes 127S and 127T reciprocate. Due to the movement of the first and second annular pistons 125S and 125T and the first and second vanes 127S and 127T, the volumes of the first and second suction chambers 131S and 131T and the first and second compression chambers 133S and 133T are continuous. The compressor 12 continuously sucks, compresses and discharges the refrigerant gas.

  As shown in FIG. 1, a lower muffler cover 170S is arranged below the lower end plate 160S, and a lower muffler chamber 180S is formed between the lower end plate 160S and the lower muffler cover 170S. And the 1st compression part 12S is opened to lower muffler room 180S. That is, a first discharge hole 190S (see FIG. 2) that connects the first compression chamber 133S of the first cylinder 121S and the lower muffler chamber 180S is provided in the vicinity of the first vane 127S of the lower end plate 160S. A first discharge valve 200S that prevents the backflow of the compressed refrigerant gas is disposed in the hole 190S.

  The lower muffler chamber 180S is one chamber formed in an annular shape, and the lower end plate 160S, the first cylinder 121S, the intermediate partition plate 140, the second cylinder 121T, and the upper end plate 160T are arranged on the discharge side of the first compression unit 12S. This is a part of the communication path that communicates with the upper muffler chamber 180T through the refrigerant path 136 (see FIG. 2) that passes through. The lower muffler chamber 180S reduces the pressure pulsation of the discharged refrigerant gas. In addition, a first discharge valve presser 201S for limiting the amount of deflection opening of the first discharge valve 200S is fixed to the first discharge valve 200S by a rivet together with the first discharge valve 200S. The first discharge hole 190S, the first discharge valve 200S, and the first discharge valve presser 201S constitute a first discharge valve portion of the lower end plate 160S.

  As shown in FIG. 1, an upper muffler cover 170T is arranged above the upper end plate 160T, and an upper muffler chamber 180T is formed between the upper end plate 160T and the upper muffler cover 170T. In the vicinity of the second vane 127T of the upper end plate 160T, a second discharge hole 190T (see FIG. 2) that communicates the second compression chamber 133T of the second cylinder 121T and the upper muffler chamber 180T is provided, and the second discharge hole 190T. Is provided with a reed valve type second discharge valve 200T for preventing the backflow of the compressed refrigerant gas. In addition, a second discharge valve presser 201T for limiting the deflection opening amount of the second discharge valve 200T is fixed to the second discharge valve 200T by a rivet together with the second discharge valve 200T. 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 presser 201T constitute a second discharge valve portion of the upper end plate 160T.

  The first cylinder 121S, the lower end plate 160S, the lower muffler cover 170S, the second cylinder 121T, the upper end plate 160T, the upper muffler cover 170T, and the intermediate partition plate 140 are integrally fastened by a plurality of through bolts 175 and the like. Out of the compression portion 12 that is integrally fastened by a through bolt 175 or the like, the outer peripheral portion of the upper end plate 160T is fixed to the compressor housing 10 by spot welding, and the compression portion 12 is fixed to the compressor housing 10. .

  The first and second through holes 101 and 102 are passed through the outer peripheral wall of the cylindrical compressor housing 10 in the axial direction and in order from the lower part in order to pass the first and second suction pipes 104 and 105. Is provided. In addition, an accumulator 25 formed of an independent cylindrical sealed container is held by an accumulator holder 252 and an accumulator band 253 on the outer side of the compressor housing 10.

  A system connection tube 255 connected to the evaporator of the refrigeration cycle is connected to the center of the top of the accumulator 25, and one end of the bottom through hole 257 provided at the bottom of the accumulator 25 extends to the upper part inside the accumulator 25. The other ends of the first and second suction pipes 104 and 105 are connected to the first and second low-pressure communication pipes 31S and 31T.

  The first and second low-pressure connecting pipes 31S, 31T for guiding the low-pressure refrigerant of the refrigeration cycle to the first and second compression parts 12S, 12T through the accumulator 25 are the first and second suction pipes 104, The first and second cylinders 121S and 121T are connected to the first and second suction holes 135S and 135T (see FIG. 2) via the 105. That is, the first and second suction holes 135S and 135T are connected in parallel to the evaporator of the refrigeration cycle.

  Connected to the top of the compressor housing 10 is a discharge pipe 107 that is connected to the refrigeration cycle and discharges high-pressure refrigerant gas to the condenser side of the refrigeration cycle. That is, the first and second discharge holes 190S and 190T are connected to the condenser of the refrigeration cycle.

  Lubricating oil is sealed in the compressor housing 10 up to the height of the second cylinder 121T. Further, the lubricating oil is sucked up from an oil supply pipe 16 attached to the lower end portion of the rotating shaft 15 by a pump blade (not shown) inserted in the lower portion of the rotating shaft 15, circulates through the compressing portion 12, and slide parts Lubrication is performed and a small gap in the compression portion 12 is sealed.

  Next, with reference to FIG.3 and FIG.4, the characteristic structure of the rotary compressor 1 of an Example is demonstrated. The rotary compressor 1 of an Example is used for a domestic air conditioner. As shown in FIG. 3, the intermediate partition plate 140 includes a vertical injection hole 141 communicating with the first and second working chambers 130 </ b> S and 130 </ b> T of the first and second compression units 12 </ b> S and 12 </ b> T, and an injection hole 141. A horizontal hole 142 for fitting the tip of the injection tube 144 for performing liquid injection (in this embodiment, liquid injection is performed, but gas injection may be performed). Is provided. An injection communication pipe 146 is connected to the rear part of the injection pipe 144 when the refrigeration cycle is assembled.

As shown in FIG. 4, the intermediate partition plate 140 has α = clockwise from the top dead center position of the second annular piston 125T (when the eccentric direction of the second eccentric portion 152T faces the position of the second vane 127T). An injection hole 141 is provided at a position rotated by 305 °. The distance from the central axis to the injection hole 141 is β = 22 mm, and the diameter of the injection hole 141 is φ ₁ = 1.2 mm. Although not shown, the inner diameters of the first and second cylinders 121S and 121T are φ ₂ = 56 mm, the outer diameters of the first and second annular pistons 125S and 125T are φ ₃ = 46 mm, and the first and second eccentric portions. The amount of eccentricity of 152S and 152T is h = 5 mm. Further, the eccentric direction of the first eccentric portion 152S is 180 ° out of phase with the eccentric direction of the second eccentric portion 152T.

  Next, with reference to FIGS. 5-11, the opening / closing operation | movement of the injection hole 141 accompanying the revolution of the 1st and 2nd annular piston 125S, 125T in the 1st and 2nd compression parts 12S, 12T is demonstrated. . FIG. 5 is a cross-sectional view showing a state in which the second annular piston of the second compression portion revolves 50 ° clockwise from the top dead center. FIG. 6 shows the first annular piston of the first compression portion. FIG. 7 is a cross-sectional view showing a state in which the second annular piston of the second compression section has revolved 215 ° clockwise from the top dead center. FIG. 8 is a cross-sectional view showing a state in which the first annular piston of the first compression section has revolved 215 ° clockwise from the bottom dead center, and FIG. 9 shows the second compression section. FIG. 5 is a partially enlarged cross-sectional view showing a state in which the second annular piston revolves 215 ° clockwise from the top dead center and the first annular piston of the first compression portion revolves 215 ° clockwise from the bottom dead center; FIG. 10 shows a state in which the second annular piston of the second compression portion revolves 230 ° clockwise from the top dead center. Is a cross-sectional view, FIG. 11 is a cross sectional view showing the first annular piston in the first compression section was 230 ° revolved clockwise from bottom dead center.

As shown in FIG. 5, when the second annular piston 125T revolves 50 ° from the top dead center, the injection hole 141 is in a fully open state and opens to the second working chamber 130T. At this time, as shown in FIG. 6, the first annular piston 125S revolves 50 ° from the bottom dead center, the injection hole 141 is fully closed, and communication with the first working chamber 130S is cut off. According to the calculation, when the second annular piston 125T revolves from the top dead center by θ ₁ = 33 °, the injection hole 141 starts to be opened, and when θ ₂ = 47 ° revolves, the injection hole 141 is fully opened. Further, when the first annular piston 125S revolves from ω ₁ = 22 ° from the bottom dead center, the injection hole 141 starts to close, and when ω ₂ = 37 ° revolves, the injection hole 141 is fully closed.

As shown in FIGS. 7 and 9, when the second annular piston 125T revolves 215 ° from the top dead center, the injection hole 141 is in a semi-closed state, and the opening to the second working chamber 130T is in a semi-closed state. . At this time, as shown in FIGS. 8 and 9, the first annular piston 125S revolves 215 ° from the bottom dead center, the injection hole 141 is in a half-open state, and the opening to the first working chamber 130S is in a half-open state. is there. According to the calculation, when the second annular piston 125T revolves by θ ₃ = 202 ° from the top dead center, the injection hole 141 starts to close, and when θ ₄ = 217 ° revolves, the injection hole 141 is fully closed. Further, when the first annular piston 125S revolves at ω ₃ = 213 ° from the bottom dead center, the injection hole 141 starts to be opened, and when the first annular piston 125S revolves at ω ₄ = 227 °, the injection hole 141 is fully opened.

  As shown in FIG. 10, when the second annular piston 125T revolves 230 ° from the top dead center, the injection hole 141 is in a fully closed state, and communication with the second working chamber 130T is cut off. At this time, as shown in FIG. 11, the first annular piston 125S revolves 230 ° from the bottom dead center, and the injection hole 141 is in a fully open state and opens to the first working chamber 130S.

FIG. 12 is a diagram showing the opening and closing states of the injection holes accompanying the revolutions of the first and second annular pistons in the first and second compression sections, and the above description is graphed. In FIG. 12, the horizontal axis represents the revolution angles from the bottom dead center and top dead center of the annular pistons 125 </ b> S and 125 </ b> T, and the vertical axis represents the aperture ratio of the injection hole 141. As shown in FIG. 12, when the first annular piston 125S revolves from ω ₁ = 22 ° from bottom dead center, the injection hole 141 starts to close, and when ω ₂ = 37 ° revolves, the injection hole 141 is fully closed. Further, when the second annular piston 125T revolves θ ₁ = 33 ° from the top dead center, the injection hole 141 starts to be opened, and when θ ₂ = 47 ° revolves, the injection hole 141 is fully opened.

Further, when the second annular piston 125T revolves from θ ₃ = 202 ° from the top dead center, the injection hole 141 starts to close, and when θ ₄ = 217 ° revolves, the injection hole 141 is fully closed. Further, when the first annular piston 125S revolves at ω ₃ = 213 ° from the bottom dead center, the injection hole 141 starts to be opened, and when the first annular piston 125S revolves at ω ₄ = 227 °, the injection hole 141 is fully opened. As shown in FIG. 12, the revolution angle range (vertical opening angle) of the first and second annular pistons 125S, 125T, in which the injection hole 141 communicates the second working chamber 130T and the first working chamber 130S, is ω ₂ − The range is θ ₁ = θ ₄ −ω ₃ = 4 °. Further, the maximum opening ratio at the time of communication is 0.14 (14%) when the full opening is 1, and is 0.2 (20%) or less.

Next, compressors that are small-sized, medium-sized, and large-sized according to the size of the volume will be described. FIG. 13 is a view showing an opening / closing state of the injection hole accompanying the revolution of the first and second annular pistons when the diameter of the injection hole of the medium-sized model is φ ₁ = 0.8 to 1.4 mm. FIG. 15 is a view showing an opening / closing state of the injection hole accompanying the revolution of the first and second annular pistons when the diameter of the injection hole of the small model is φ ₁ = 0.8 to 1.4 mm, FIG. It is a figure which shows the opening-and-closing state of the injection hole accompanying the revolution of the 1st and 2nd annular piston when the diameter of the injection hole of a large sized model is (phi) ₁ = 0.8-1.4mm.

As shown in FIG. 13, in the rotary compressor 1 of the present invention, in the medium-sized model, the diameter φ ₁ of the injection hole 141 is 0.8 mm <φ ₁ ≦ 1.4 mm, and the injection hole 141 is the second working chamber 130T. And the first and second annular pistons 125S and 125T opened to the first working chamber 130S have a revolution angle range (upper and lower opening angles) larger than 0 ° and 6 ° or less, and an opening ratio during communication of 20% or less.

As shown in FIG. 14, the rotary compressor 1 of the present invention, in a small model, the diameter phi ₁ of 1.1 mm <phi ₁ ≦ 1.4 mm of the injection hole 141, and the injection hole 141 second actuation chamber 130T The revolution angle range (vertical opening angle) of the first and second annular pistons 125S and 125T that are opened to the first working chamber 130S is set to be greater than 0 ° and 3 ° or less, and the opening rate during communication is 20% or less.

As shown in FIG. 15, in the rotary compressor 1 of the present invention, in a large model, the diameter φ ₁ of the injection hole 141 is 0.8 mm <φ ₁ ≦ 1.4 mm, and the injection hole 141 is connected to the second working chamber 130T. The revolution angle range (vertical opening angle) of the first and second annular pistons 125S and 125T that are opened to the first working chamber 130S is set to be greater than 0 ° and 6 ° or less, and the opening ratio during communication is 20% or less.

In summary, the rotary compressor 1 of the present invention is a compact model-large models, the diameter phi ₁ of 0.8 mm <phi ₁ ≦ 1.4 mm of the injection hole 141, and the injection hole 141 second actuation chamber 130T The revolution angle range (vertical opening angle) of the first and second annular pistons 125S and 125T that are opened to the first working chamber 130S is set to be greater than 0 ° and 6 ° or less, and the opening ratio during communication is 20% or less.

According to the present invention, since the diameter φ ₁ of the injection hole 141 is increased to 0.8 mm <φ ₁ ≦ 1.4 mm, a necessary injection flow rate can be ensured and the hole processing is easy. In addition, the revolution angle range (vertical opening angle) of the first and second annular pistons 125S and 125T that opens the injection hole 141 to the second working chamber 130T and the first working chamber 130S is greater than 0 ° and less than or equal to 6 °. Since the aperture ratio at that time is 20% or less, the region where the injection holes 141 can be arranged is wide. In addition, since the opening ratio of the injection hole 141 when the first and second working chambers 130S and 130T communicate with each other is set to 20% or less, the leakage of the compressed refrigerant gas from the high pressure working chamber to the low pressure working chamber is prevented. It doesn't matter.

DESCRIPTION OF SYMBOLS 1 Rotary compressor 10 Compressor housing | casing 11 Motor 12 Compression part 15 Rotating shaft 25 Accumulator 31S 1st low pressure connection pipe 31T 2nd low pressure connection pipe 101 1st through-hole 102 2nd through-hole 104 1st suction pipe 105 2nd suction | inhalation Pipe 107 Discharge pipe (discharge part)
111 Stator 112 Rotor 12S 1st compression part 12T 2nd compression part 121S 1st cylinder 121T 2nd cylinder 122S 1st lateral extension part 122T 2nd lateral extension part 123S 1st cylinder inner wall 123T 2nd cylinder inner wall 124S 1st 1 spring hole 124T second spring hole 125S first annular piston 125T second annular piston 127S first vane 127T second vane 128S first vane groove 128T second vane groove 129S first pressure introduction path 129T second pressure introduction path 130S first 1st working chamber 130T 2nd working chamber 131S 1st suction chamber 131T 2nd suction chamber 133S 1st compression chamber 133T 2nd compression chamber 135S 1st suction hole 135T 2nd suction hole 136 Refrigerant passage 140 intermediate partition plate 141 injection hole 142 side Hole 144 Injection pipe 146 Injection communication pipe 151 Subshaft portion 152S First eccentric portion 152T Second eccentric portion 153 Main shaft portion 160S Lower end plate 160T Upper end plate 161S Sub bearing portion 161T Main bearing portion 170S Lower muffler cover 170T Upper muffler cover 175 Through bolt 180S Lower muffler chamber 180T Upper muffler chamber 190S First discharge hole 190T Second discharge hole 200S First discharge valve 200T Second discharge valve 201S First discharge valve press 201T Second discharge valve press 252 Accum holder 253 Accum band 255 System connection pipe 257 Bottom through-hole R Opening

Claims (2)

A vertically-placed cylindrical compressor housing which is provided with a refrigerant discharge part at the top and a refrigerant suction part at the bottom and sealed;
A lower upper end plate disposed at a lower portion of the compressor housing, having annular first and second cylinders, a bearing portion and a discharge valve portion, and closing the end portions of the first and second cylinders; An intermediate partition plate arranged between the first and second cylinders and partitioning between them, and the first and second cylinders of the first and second cylinders fitted to the first and second eccentric parts of the rotating shaft supported by the bearing part First and second annular pistons that revolve around the cylinder along the inner peripheral surface to form first and second working chambers between the cylinder inner peripheral surface and the first and second cylinders. The first and second vane grooves protrude into the first and second working chambers and come into contact with the first and second annular pistons, and the first and second working chambers are connected to the first and second suction chambers. First and second vanes partitioned into a first compression chamber and a second compression chamber, and cooled through the suction portion. First and second compression unit sucks the refrigerant from the low pressure side of the cycle, and discharges refrigerant from the discharge portion through the compressor housing,
A motor that is installed in an upper part of the compressor housing and drives the compression unit via the rotating shaft;
A rotary compressor comprising:
The intermediate partition plate is fitted with a vertical injection hole communicating with the first and second working chambers and an injection pipe communicating with the injection holes for injecting refrigerant into the first and second working chambers. Provided with a horizontal hole,
The diameter of the injection hole is in the range of φ1.4 mm to φ1.4 mm,
The first and second annular pistons revolve in the first and second cylinders to open and close the injection hole, and the first and second opening the injection hole to both the first and second working chambers. The revolution angle range of the two annular pistons is set to a range of 0 ° to 6 °,
A rotary compressor characterized by that.   2. The rotary compressor according to claim 1, wherein an opening ratio of the injection holes when the injection holes are opened in both the first and second working chambers is 20% or less.

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