JP2017089648A - Rotary Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent an efficiency of a rotary compressor from being reduced by restricting an inverse flow of refrigerant compressed by an upper cylinder at a refrigerant passage hole.SOLUTION: A rotary compressor of this invention is configured in such a way that a lower end plate cover is formed into a flat plate shape, the lower end plate is formed with a lower discharging chamber concave part to cause the lower end plate to overlap a lower discharging hole side, the lower discharging chamber concave part is formed within a fan-shaped range between a first diameter passing through a middle point of a line connecting a center of a sub-bearing part, a center of the lower discharging hole and a center of a lower rivet and a second diameter opened by a pitch angle of 90° toward the lower discharging hole with the center of the sub-bearing part being applied as a center, the lower end plate cover chamber is constituted by a concave part of the lower discharging chamber and a concave part for storing the lower discharging valve. The refrigerant passage hole is arranged while being communicated with the concave part of the lower discharging chamber at a position of the outer peripheral side of the lower end plate and also at a position inside the inner peripheral wall of the concave part of the lower discharging chamber.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a two-cylinder rotary compressor used in an air conditioner.

  For example, in Patent Document 1, in a two-cylinder rotary compressor, high-temperature compressed refrigerant that is compressed by a lower cylinder and discharged from a lower discharge hole is transferred from a lower end plate cover chamber (lower muffler chamber) to an upper end plate cover chamber (upper By arranging the refrigerant passage hole flowing toward the muffler chamber) at a position away from the suction chamber side of the lower cylinder and the upper cylinder, the compressed refrigerant heats the suction refrigerant on the suction chamber side of the lower cylinder and the upper cylinder. The technique which suppresses this and improves compressor efficiency is described.

  Further, in Patent Document 2, high-temperature compressed refrigerant that is compressed in the lower cylinder and discharged from the lower discharge hole suppresses heating of the refrigerant drawn in the suction chamber of the lower cylinder by heating the lower end plate. Techniques for improving the performance are described.

JP 2014-145318 A International Publication No. 2013/094114

  In the rotary compressor described in Patent Document 1, the lower end plate cover chamber formed between the lower end plate and the lower end plate cover has a large volume by inflating the lower end plate cover (lower muffler cover). Therefore, the amount of the refrigerant that is compressed by the upper cylinder, discharged from the upper discharge hole, flows backward through the refrigerant passage hole, and flows into the lower muffler chamber is large.

  In the rotary compressor described in Patent Document 2, the refrigerant passage hole is disposed on the opposite side of the lower discharge valve housing portion with respect to the lower discharge hole provided in the lower end plate, and the refrigerant discharged from the lower discharge hole is lowered. Since it flows into the refrigerant passage hole through the discharge valve accommodating portion, it is necessary to deepen the lower discharge valve accommodating portion. Therefore, the volume of the lower end plate cover chamber (refrigerant discharge space) is increased, and the amount of refrigerant compressed by the upper cylinder and discharged from the upper discharge hole and flowing backward through the refrigerant passage hole and flowing into the lower muffler chamber is large.

  Hereinafter, the backflow phenomenon of the refrigerant will be described. In a two-cylinder rotary compressor, in order to minimize the torque fluctuation per rotation of the rotating shaft as much as possible, in general, the steps of suction, compression, and discharge are performed by two cylinders with phases different by 180 °. Yes. Except for special operating conditions such as when starting up, in the operation of the air conditioner at normal outdoor temperature and indoor temperature, the discharge process of one cylinder is about 1/3 during one rotation. Therefore, 1/3 in one rotation is the discharge process of one cylinder (process in which the discharge valve is opened), the other 1/3 is the discharge process of the other cylinder, and the remaining 1/3 is both This is a process in which the discharge valve is closed.

  Here, when both the discharge valves of the two cylinders are closed and there is no flow of refrigerant discharged from the compression chamber, the upper end plate cover chamber, the lower end plate cover chamber, the inside of the compressor casing outside the upper end plate cover chamber, Same pressure. In the discharge process of one of the cylinders, the pressure in the compression chamber that is the most upstream in the flow of the refrigerant is the highest in the compressed high pressure region, and then the upper end plate cover chamber and the compressor casing outside the upper end plate cover chamber In order. Therefore, immediately after the discharge valve of the upper cylinder is opened, the pressure in the upper end plate cover chamber becomes higher than the pressure in the compressor casing outside the upper end plate cover chamber and in the lower end plate cover chamber. Therefore, at the next moment, the refrigerant flows into the lower muffler chamber by flowing backward from the upper end plate cover chamber into the compressor casing and the refrigerant passage hole outside the upper end plate cover chamber.

  The flow of the refrigerant from the upper end plate cover chamber into the compressor casing outside the upper end plate cover chamber is the original flow, but the refrigerant flowing from the upper end plate cover chamber to the lower end plate cover chamber is discharged from the upper cylinder. After the end of the process, the refrigerant flows again through the refrigerant passage hole and the upper end plate cover chamber and into the compressor casing outside the upper end plate cover chamber. There is a problem of reducing efficiency.

  Moreover, the rotary compressor described in patent document 2 is suppressing that the lower end plate which covers the lower surface of a lower cylinder with the refrigerant | coolant compressed with the lower cylinder is heated. However, in the rotary compressor, particularly when the outside air has been stopped for a long time in a low temperature atmosphere, the liquefied refrigerant may accumulate in the compressor housing. Since the density of the liquid refrigerant at a low temperature is larger than the density of the lubricating oil, the liquid refrigerant accumulates at the lowermost part inside the compressor housing. When the rotary compressor is started in this state, the liquid refrigerant is sucked up by the oil supply blades from the lower end of the rotating shaft. If the liquid refrigerant is sucked up, the viscosity of the liquid refrigerant is smaller than the viscosity of the lubricating oil, so that the sliding part of the compression part may be poorly lubricated and damaged.

  Therefore, at the time of starting the rotary compressor, it is necessary to quickly heat and vaporize the liquid refrigerant. However, if the heating of the lower end plate is suppressed as in the rotary compressor described in Patent Document 2, the compressor Vaporization due to heating of the liquid refrigerant accumulated in the lower part of the housing is suppressed, and the problem is that the liquid refrigerant is sucked up by the oil supply blades and damage due to poor lubrication of the compression unit occurs.

  Further, in the rotary compressor, a part of the lubricating oil is caught in the refrigerant inside the compressor casing and discharged out of the compressor casing, and the discharged lubricating oil is the refrigerant circuit (refrigeration cycle) of the air conditioner. Is taken into the lower cylinder and the upper cylinder together with the suction refrigerant. The lubricating oil sucked into the lower cylinder is discharged together with the refrigerant from the lower discharge hole into the lower end plate cover chamber. When the lubricating oil discharged into the lower end plate cover chamber accumulates in the lower end plate cover chamber and the lower discharge hole is immersed in the lubricating oil, there arises a problem that the discharge resistance of the refrigerant becomes low and the efficiency is reduced and noise is generated. This problem tends to occur as the volume of the lower end plate cover chamber decreases.

  An object of the present invention is to prevent the refrigerant compressed by the upper cylinder from flowing back through the refrigerant passage hole, thereby preventing a reduction in the efficiency of the rotary compressor.

  The present invention provides a vertically mounted cylindrical compressor housing which is provided with an upper suction pipe and a lower suction pipe which are provided with a discharge pipe for discharging a refrigerant at the upper part and with which a refrigerant is sucked at a lower part of the side surface, and the compressor casing. An accumulator fixed to the side of the body and connected to the upper suction pipe and the lower suction pipe, a motor disposed in the compressor housing, and disposed below the motor in the compressor housing and driven by the motor And a compression part that sucks and compresses the refrigerant from the accumulator through the upper suction pipe and the lower suction pipe and discharges the refrigerant from the discharge pipe, and the compression part includes an annular upper cylinder and a lower cylinder, An upper end plate for closing the upper side of the upper cylinder, a lower end plate for closing the lower side of the lower cylinder, and a lower side of the upper cylinder and the upper side of the lower cylinder, which are disposed between the upper cylinder and the lower cylinder. Intermediate A rotating shaft supported by a cutting plate, a main bearing portion provided on the upper end plate, and a sub bearing portion provided on the lower end plate and rotated by the motor, and a phase difference of 180 ° between the rotating shaft and each other. An upper eccentric portion and a lower eccentric portion provided on the upper piston, an upper piston fitted into the upper eccentric portion and revolved along an inner peripheral surface of the upper cylinder to form an upper cylinder chamber in the upper cylinder, A lower piston fitted into the lower eccentric part and revolves along the inner peripheral surface of the lower cylinder to form a lower cylinder chamber in the lower cylinder, and an upper vane groove provided in the upper cylinder into the upper cylinder chamber An upper vane that protrudes into contact with the upper piston and divides the upper cylinder chamber into an upper suction chamber and an upper compression chamber, and protrudes into the lower cylinder chamber from a lower vane groove provided in the lower cylinder and contacts the lower piston. The lower siri An upper end plate cover chamber is formed between the lower vane that divides the chamber into a lower suction chamber and a lower compression chamber, and the upper end plate so as to cover the upper end plate, and the interior of the upper end plate cover chamber and the compressor housing An upper end plate cover having an upper end plate cover discharge hole communicating therewith, a lower end plate cover that covers the lower end plate and forms a lower end plate cover chamber between the lower end plate, and the upper compression provided in the upper end plate An upper discharge hole for communicating the chamber and the upper end plate cover chamber, a lower discharge hole provided in the lower end plate for communicating the lower compression chamber and the lower end plate cover chamber, the lower end plate, the lower cylinder, In the rotary compressor provided with an intermediate partition plate, the upper end plate, and the upper cylinder, and a refrigerant passage hole communicating with the lower end plate cover chamber and the upper end plate cover chamber, the upper discharge provided in the upper end plate Upper spout extending in the shape of a groove from the position of the hole A valve receiving recess, a lower discharge valve receiving recess provided in the lower end plate and extending in a groove shape from the position of the lower discharge hole, a rear end portion fixed by an upper rivet in the upper discharge valve receiving recess, and a front portion A reed valve type upper discharge valve that opens and closes the upper discharge hole and a rear end portion are overlapped with the upper discharge valve, fixed in the upper discharge valve housing recess by the upper rivet, and a front portion is warped, and the upper discharge valve An upper discharge valve presser that regulates the degree of opening, and a reed valve type lower discharge valve and a rear end portion whose rear end portion is fixed by a lower rivet in the lower discharge valve housing recess and whose front portion opens and closes the lower discharge hole Is overlapped with the lower discharge valve and fixed in the lower discharge valve housing recess by the lower rivet, and the front part is warped to regulate the opening of the lower discharge valve and accommodated in the lower discharge valve housing recess. A lower discharge valve presser, and the lower end plate cover is formed in a flat plate shape. A lower discharge chamber recess is formed in the lower end plate so as to overlap the lower discharge hole side of the lower discharge valve housing recess, and the lower discharge chamber recess has a center of the auxiliary bearing portion and the lower discharge hole. A first diameter line passing through the center of the line segment connecting the center of the lower rivet and the second diameter opened at a pitch angle of 90 ° in the direction of the lower discharge hole with the center of the auxiliary bearing portion as the center The lower end plate cover chamber is formed by the lower discharge chamber recess and the lower discharge valve housing recess, and the refrigerant passage hole is formed with respect to the lower discharge hole. The lower discharge plate is disposed on the outer peripheral side of the lower end plate and inside the inner peripheral wall of the lower discharge chamber recess so as to communicate with the lower discharge chamber recess.

  The present invention can prevent the refrigerant compressed by the lower cylinder from flowing backward through the refrigerant passage hole and prevent a reduction in the efficiency of the rotary compressor.

FIG. 1 is a longitudinal sectional view showing a first embodiment of a rotary compressor according to the present invention. FIG. 2 is an upper exploded perspective view illustrating a compression unit of the rotary compressor according to the first embodiment. FIG. 3 is an upper exploded perspective view showing the rotating shaft and the oil supply blades of the rotary compressor of the first embodiment. FIG. 4 is a bottom view showing a lower end plate of the rotary compressor of the first embodiment. FIG. 5 is a longitudinal cross-sectional view showing a lower discharge valve accommodating recess to which the lower discharge valve of the rotary compressor of the first embodiment is attached. FIG. 6 is a longitudinal cross-sectional view showing a lower discharge valve housing recess in which the lower discharge valve of the rotary compressor of the second embodiment is attached. FIG. 7 is a longitudinal cross-sectional view showing a lower discharge valve accommodating recess to which a lower discharge valve of the rotary compressor of the third embodiment is attached. FIG. 8 is a bottom view showing a lower end plate of the rotary compressor of the fourth embodiment. FIG. 9 is a bottom view of the lower end plate of the rotary compressor of the fifth embodiment. FIG. 10 is a lower perspective view illustrating the lower end plate of the rotary compressor of the sixth embodiment. FIG. 11 is a bottom view illustrating a state in which the lower end plate and the lower end plate cover of the rotary compressor according to the seventh embodiment are overlapped.

  EMBODIMENT OF THE INVENTION Below, the form (Example) for implementing this invention is demonstrated in detail, referring drawings.

  1 is a longitudinal sectional view showing Embodiment 1 of a rotary compressor according to the present invention, FIG. 2 is an upper exploded perspective view showing a compression section of the rotary compressor of Embodiment 1, and FIG. FIG. 3 is an exploded top perspective view showing a rotation shaft and oil supply blades of the rotary compressor according to the first embodiment.

  As shown in FIG. 1, the rotary compressor 1 includes a compression unit 12 disposed at a lower portion in a sealed vertical cylindrical compressor housing 10, a compression unit 12 disposed above the compression unit 12, and a rotating shaft 15. A motor 11 that drives the compression unit 12 through the vertical axis, and a vertical cylindrical accumulator 25 that is fixed to a side portion of the compressor housing 10.

  The accumulator 25 is connected to the upper suction chamber 131T (see FIG. 2) of the upper cylinder 121T via the upper suction pipe 105 and the accumulator upper L-shaped pipe 31T, and is connected to the lower side via the lower suction pipe 104 and the lower L-shaped pipe 31S of the accumulator. The cylinder 121S is connected to the lower suction chamber 131S (see FIG. 2).

  The motor 11 includes a stator 111 on the outer side and a rotor 112 on the inner side. The stator 111 is shrink-fitted and fixed to the inner peripheral surface of the compressor housing 10, and the rotor 112 is fixed to the rotary shaft 15 by shrink-fitting. Yes.

  The rotary shaft 15 is supported by a secondary shaft portion 151 below the lower eccentric portion 152S being rotatably fitted to a secondary bearing portion 161S provided on the lower end plate 160S, and a main shaft portion 153 above the upper eccentric portion 152T. An upper eccentric portion 152T and a lower eccentric portion 152S, which are rotatably fitted to and supported by a main bearing portion 161T provided on the upper end plate 160T and are provided with a phase difference of 180 degrees from each other, are respectively provided with an upper piston 125T and a lower By being rotatably fitted to the piston 125S, the entire compression portion 12 is rotatably supported, and the upper piston 125T and the lower piston 125S are respectively rotated on the inner peripheral surfaces of the upper cylinder 121T and the lower cylinder 121S. Revolve along.

  Lubricating oil 18 is contained in the compressor housing 10 for lubricating the sliding portion of the compression portion 12 and sealing the upper compression chamber 133T (see FIG. 2) and the lower compression chamber 133S (see FIG. 2). 12 is enclosed in an amount that substantially immerses 12. An attachment leg 310 that fixes a plurality of elastic support members (not shown) that support the entire rotary compressor 1 is fixed to the lower side of the compressor housing 10.

  As shown in FIG. 2, the compression unit 12 includes an upper end plate cover 170T having a dome-shaped bulging portion from above, an upper end plate 160T, an upper cylinder 121T, an intermediate partition plate 140, a lower cylinder 121S, a lower end plate 160S, and a flat plate shape. The lower end plate cover 170S is laminated. The entire compression unit 12 is fixed by a plurality of through bolts 174 and 175 and auxiliary bolts 176 arranged substantially concentrically from above and below.

  An annular upper cylinder 121T is provided with an upper suction hole 135T that fits into the upper suction pipe 105. The annular lower cylinder 121S is provided with a lower suction hole 135S that fits into the lower suction pipe 104. An upper piston 125T is disposed in the upper cylinder chamber 130T of the upper cylinder 121T. A lower piston 125S is disposed in the lower cylinder chamber 130S of the lower cylinder 121S.

  The upper cylinder 121T is provided with an upper vane groove 128T extending radially outward from the upper cylinder chamber 130T, and an upper vane 127T is disposed in the upper vane groove 128T. The lower cylinder 121S is provided with a lower vane groove 128S extending radially outward from the lower cylinder chamber 130S, and a lower vane 127S is disposed in the lower vane groove 128S.

  The upper cylinder 121T is provided with an upper spring hole 124T at a position that does not penetrate the upper cylinder chamber 130T at a position overlapping the upper vane groove 128T from the outer surface, and the upper spring 126T is disposed in the upper spring hole 124T. The lower cylinder 121S is provided with a lower spring hole 124S at a position that does not penetrate the lower cylinder chamber 130S at a position overlapping the lower vane groove 128S from the outer surface, and a lower spring 126S is disposed in the lower spring hole 124S.

  The upper cylinder chamber 130T is closed at the top and bottom by an upper end plate 160T and an intermediate partition plate 140, respectively. The lower cylinder chamber 130S is closed at the top and bottom by an intermediate partition plate 140 and a lower end plate 160S, respectively.

  The upper cylinder chamber 130T includes an upper suction chamber 131T communicating with the upper suction hole 135T and an upper plate 160T provided by the upper vane 127T being pressed by the upper spring 126T and coming into contact with the outer peripheral surface of the upper piston 125T. The upper compression chamber 133T communicated with the discharge hole 190T. The lower cylinder chamber 130S includes a lower suction chamber 131S communicating with the lower suction hole 135S and a lower plate provided in the lower end plate 160S when the lower vane 127S is pressed by the lower spring 126S and comes into contact with the outer peripheral surface of the lower piston 125S. And a lower compression chamber 133S communicating with the discharge hole 190S.

  The upper end plate 160T is provided with an upper discharge hole 190T that penetrates the upper end plate 160T and communicates with the upper compression chamber 133T of the upper cylinder 121T, and an annular shape surrounding the upper discharge hole 190T is provided on the outlet side of the upper discharge hole 190T. An upper valve seat (not shown) is formed. The upper end plate 160T is formed with an upper discharge valve accommodating recess 164T extending in a groove shape from the position of the upper discharge hole 190T in the circumferential direction of the upper end plate 160T.

  The upper discharge valve accommodating recess 164T has a reed valve type upper discharge valve 200T and a rear end whose rear end is fixed by an upper rivet 202T in the upper discharge valve accommodating recess 164T and whose front opens and closes the upper discharge hole 190T. The upper discharge valve holder 201T as a whole is placed on the upper discharge valve 200T and fixed in the upper discharge valve housing recess 164T by the upper rivet 202T, and the front part is curved (warped) to regulate the opening degree of the upper discharge valve 200T. Contained.

  The lower end plate 160S is provided with a lower discharge hole 190S that penetrates the lower end plate 160S and communicates with the lower compression chamber 133S of the lower cylinder 121S, and an annular shape surrounding the lower discharge hole 190S is provided on the outlet side of the lower discharge hole 190S. A lower valve seat 191S (see FIG. 4) is formed. The lower end plate 160S is formed with a lower discharge valve accommodating recess 164S (see FIG. 4) extending from the position of the lower discharge hole 190T in a groove shape in the circumferential direction of the lower end plate 160S.

  The lower discharge valve accommodating recess 164S has a reed valve type lower discharge valve 200S and a rear end that are fixed by a lower rivet 202S in the lower discharge valve accommodating recess 164S and the front portion opens and closes the lower discharge hole 190S. All of the lower discharge valve presser 201S that overlaps with the lower discharge valve 200S and is fixed in the lower discharge valve housing recess 164S by the lower rivet 202S and the front part is curved (warped) to regulate the opening degree of the lower discharge valve 200S. Is housed.

  An upper-end plate cover chamber 180T is formed between the upper-end plate 160T and the upper-end plate cover 170T having a dome-shaped bulge. A lower end plate cover chamber 180S is formed between the lower end plate 160S and the flat lower end plate cover 170S that are closely fixed to each other (details of the lower end plate cover chamber 180S will be described later). A refrigerant passage hole 136 that penetrates the lower end plate 160S, the lower cylinder 121S, the intermediate partition plate 140, the upper end plate 160T, and the upper cylinder 121T and communicates the lower end plate cover chamber 180S and the upper end plate cover chamber 180T is provided.

  As shown in FIG. 3, the rotary shaft 15 is provided with an oil supply vertical hole 155 that penetrates from the lower end to the upper end, and an oil supply blade 158 is press-fitted into the oil supply vertical hole 155. In addition, a plurality of oil supply lateral holes 156 communicating with the oil supply vertical holes 155 are provided on the side surface of the rotating shaft 15.

  Below, the flow of the refrigerant | coolant by rotation of the rotating shaft 15 is demonstrated. In the upper cylinder chamber 130T, the upper piston 125T fitted to the upper eccentric portion 152T of the rotary shaft 15 is rotated along the outer peripheral surface of the upper cylinder chamber 130T (the inner peripheral surface of the upper cylinder 121T) by the rotation of the rotary shaft 15. Thus, the upper suction chamber 131T sucks refrigerant from the upper suction pipe 105 while expanding the volume, and the upper compression chamber 133T compresses the refrigerant while reducing the volume, and the pressure of the compressed refrigerant is changed to the upper discharge valve. When the pressure is higher than the pressure in the upper end plate cover chamber 180T outside the 200T, the upper discharge valve 200T is opened and the refrigerant is discharged from the upper compression chamber 133T to the upper end plate cover chamber 180T. The refrigerant discharged into the upper end plate cover chamber 180T is discharged into the compressor housing 10 from an upper end plate cover discharge hole 172T (see FIG. 1) provided in the upper end plate cover 170T.

  Further, in the lower cylinder chamber 130S, the lower piston 125S fitted to the lower eccentric portion 152S of the rotary shaft 15 by the rotation of the rotary shaft 15 causes the outer peripheral surface of the lower cylinder chamber 130S (the inner peripheral surface of the lower cylinder 121S). ), The lower suction chamber 131S sucks in the refrigerant from the lower suction pipe 104 while increasing the volume, and the lower compression chamber 133S compresses the refrigerant while reducing the volume, and the pressure of the compressed refrigerant is reduced. When the pressure in the lower end plate cover chamber 180S outside the lower discharge valve 200S becomes higher, the lower discharge valve 200S opens and the refrigerant is discharged from the lower compression chamber 133S to the lower end plate cover chamber 180S. The refrigerant discharged into the lower end plate cover chamber 180S passes through the refrigerant passage hole 136 and the upper end plate cover chamber 180T, and passes through the upper end plate cover discharge hole 172T (see FIG. 1) provided in the upper end plate cover 170T. It is discharged inside.

  The refrigerant discharged into the compressor housing 10 is a notch (not shown) provided on the outer periphery of the stator 111 that communicates with the upper and lower sides, a gap (not shown) between winding portions of the stator 111, or the stator 111. Is guided to the upper side of the motor 11 through the gap 115 (see FIG. 1) between the rotor 112 and the rotor 112, and is discharged from the discharge pipe 107 at the top of the compressor housing 10.

  Hereinafter, the flow of the lubricating oil 18 will be described. The lubricating oil 18 passes from the lower end of the rotary shaft 15 through the oil supply vertical hole 155 and the plurality of oil supply horizontal holes 156, and slides between the sub bearing portion 161S and the sub shaft portion 151 of the rotary shaft 15, the main bearing portion 161T, Oil is supplied to the sliding surface of the rotating shaft 15 with the main shaft portion 153, the sliding surface of the lower eccentric portion 152S of the rotating shaft 15 and the lower piston 125S, and the sliding surface of the upper eccentric portion 152T and the upper piston 125T, respectively. Lubricate the sliding surface.

  The oil supply blade 158 sucks up the lubricating oil 18 by applying a centrifugal force to the lubricating oil 18 in the oil supply vertical hole 155, and the lubricating oil 18 is discharged from the compressor housing 10 together with the refrigerant to lower the oil level. In addition, the lubricant 18 is surely supplied to the sliding surface.

  Next, a characteristic configuration of the rotary compressor 1 according to the first embodiment will be described. FIG. 4 is a bottom view showing a lower end plate of the rotary compressor of the first embodiment, and FIG. 5 is a longitudinal sectional view showing a lower discharge valve housing concave portion to which the lower discharge valve of the rotary compressor of the first embodiment is attached. is there.

As shown in FIG. 4, the lower end plate cover chamber 180S has a lower discharge plate chamber provided in the lower end plate 160S because the lower end plate cover 170S has a flat plate shape and does not have a dome-like bulge portion like the upper end plate cover 170T. It is comprised by the recessed part 163S and the lower discharge valve accommodation recessed part 164S. Lower discharge valve housing recess 164S from the position of the lower discharge holes 190S, a direction which intersects the radial line _{L 1} connecting the center _{O 2} of the center _{O 1} and the lower discharge holes 190S sub bearing portion 161S, in other words, the lower end plate The groove extends linearly in the circumferential direction of 160S. The lower discharge valve housing recess 164S is connected to the lower discharge chamber recess 163S. The lower discharge valve accommodating recess 164S is formed to have a width slightly larger than the width of the lower discharge valve 200S and the lower discharge valve presser 201S, and accommodates the lower discharge valve 200S and the lower discharge valve presser 201S, and the lower discharge valve 200S and The lower discharge valve holder 201S is positioned.

  The lower discharge chamber recess 163S is formed to the same depth as the lower discharge valve storage recess 164S so as to overlap the lower discharge hole 190S side of the lower discharge valve storage recess 164S. The lower discharge hole 190S side of the lower discharge valve housing recess 164S is housed in the lower discharge chamber recess 163S.

Lower discharge chamber recess 163S includes a center _{O 1} of the sub bearing portion 161S, the midpoint _{O 4} of the line segment _{L 2} (length F) connecting the center _{O 2} and the center _{O 3} of below rivets 202S of the lower discharge holes 190S , a radial line L ₃ through the form in the sector ranging between radial line L ₄ open pitch angle 90 ° to the direction of the lower discharge holes 190S around the center O ₁ of the sub bearing portion 161S. The refrigerant passage hole 136 is disposed at a position where at least a part thereof overlaps with the lower discharge chamber recess 163S and communicates with the lower discharge chamber recess 163S.

  As shown in FIG. 5, an annular lower valve seat 191 </ b> S that is raised with respect to the bottom of the lower discharge chamber recess 163 </ b> S is formed at the periphery of the opening of the lower discharge hole 190 </ b> S, and the lower valve seat 191 </ b> S is the lower discharge valve 200 </ b> S. Abuts the front. The depth H to the lower valve seat 191S of the lower discharge chamber recess 163S is 1.5 times or less the diameter φD1 of the lower discharge hole 190S.

  The opening degree of the lower discharge valve 200S when the refrigerant is discharged from the lower discharge hole 190S, that is, the lift amount of the lower discharge valve 200S with respect to the lower valve seat 191S needs to be a lift amount that does not become the resistance of the discharge flow. Therefore, the depth H to the lower valve seat 160S of the lower discharge chamber recess 163S needs to be determined in consideration of the lift amount of the lower discharge valve 200S and the thicknesses of the lower discharge valve 200S and the lower discharge valve presser 201S. However, 1.5 times the diameter φD1 of the lower discharge hole 190S is sufficient.

  The refrigerant passage hole 136 is disposed at a position where at least a part thereof overlaps with the upper discharge chamber recess 163T and communicates with the upper discharge chamber recess 163T. The upper discharge chamber recess 163T and the upper discharge valve accommodating recess 164T formed in the upper end plate 160T are not shown in detail, but the lower discharge chamber recess 163S and the lower discharge valve accommodating recess 164S formed in the lower end plate 160S, It is formed in the same shape. The upper end plate cover chamber 180T is constituted by a dome-shaped bulged portion of the upper end plate cover 170T, an upper discharge chamber recess 163T, and an upper discharge valve housing recess 164T.

  With the configuration of the rotary compressor 1 according to the first embodiment described above, the distance between the lower discharge hole 190S and the inlet of the refrigerant passage hole 136 can be shortened. Therefore, the volume of the lower end plate cover chamber 180S, that is, the sum of the volume of the lower discharge chamber recess 163S and the volume of the lower discharge valve housing recess 164S can be significantly reduced as compared with the conventional case. As a result, the refrigerant compressed by the upper cylinder 121T and discharged from the upper discharge hole 190T can flow back into the lower end plate cover chamber 180S through the refrigerant passage hole 136, thereby reducing the efficiency of the rotary compressor 1. Decline can be prevented.

FIG. 6 is a longitudinal cross-sectional view showing a lower discharge valve housing recess in which the lower discharge valve of the rotary compressor of the second embodiment is attached. As shown in FIG. 6, in the rotary compressor 1 of the second embodiment, the depth H ₂ to the lower valve seat 191S of the lower discharge chamber recess 163S2 and the lower discharge valve housing recess 164S2 formed in the lower end plate 160S2 is It is made shallow compared with the depth H to the lower valve seat 191S of the lower discharge chamber recessed part 163S and the lower discharge valve accommodation recessed part 164S formed in the lower end plate 160S of the rotary compressor 1 of Example 1. The lower end plate cover 170S2 has a recess 171S2 at a portion facing the front portion of the lower discharge valve retainer 201S, and accommodates a portion where the front portion of the lower discharge valve retainer 201S protrudes from the lower discharge chamber recess 163S2. The depth from the recess 171S2 to the lower valve seat 191S is formed to be 1.5 times or less the diameter φD1 of the lower discharge hole 190S.

  Due to the configuration of the rotary compressor 1 of the second embodiment described above, the volume of the lower discharge valve accommodating recess 164S2 can be made smaller than that of the rotary compressor 1 of the first embodiment, and thus the compressed by the upper cylinder 121T. The flow rate of the refrigerant discharged from the upper discharge hole 190T backflowing through the refrigerant passage hole 136 and flowing into the lower end plate cover chamber 180S2 can be further reduced, and a reduction in the efficiency of the rotary compressor 1 can be prevented.

  FIG. 7 is a longitudinal cross-sectional view showing a lower discharge valve accommodating recess to which a lower discharge valve of the rotary compressor of the third embodiment is attached. As shown in FIG. 7, in the rotary compressor 1 according to the third embodiment, the front end portion of the lower discharge valve presser 201S3 is formed so that the thickness of the portion adjacent to the lower end plate cover 170S is thinner than the thickness of the other portions. Yes. Thus, the depth H2 to the lower valve seat 191S of the lower discharge chamber recess 163S3 and the lower discharge valve housing recess 164S3 is secured while securing the same opening as the lower discharge valve 201S of the rotary compressor 1 of the first embodiment. Like shallow.

  With the configuration of the rotary compressor 1 of the third embodiment described above, the volume of the lower end plate cover chamber 180S3 can be made smaller than the rotary compressor 1 of the second embodiment by the volume of the recess 171S2 of the second embodiment. Thus, the refrigerant compressed by the upper cylinder 121T and discharged from the upper discharge hole 190T can flow back into the lower end plate cover chamber 180S3 through the refrigerant passage hole 136, thereby further reducing the rotary compressor. 1 can be prevented.

FIG. 8 is a bottom view showing a lower end plate of the rotary compressor of the fourth embodiment. As shown in FIG. 8, in the rotary compressor 1 of the fourth embodiment, the refrigerant passage hole 136N provided in the lower end plate 160S4 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T) The diameter is smaller than the refrigerant passage hole 136 of the rotary compressor 1 of the first embodiment, and two are provided (may be three or more). The total cross-sectional area of the two (or three or more) refrigerant passage holes 136N is equal to the cross-sectional area of the refrigerant passage hole 136 of the rotary compressor 1 of the first embodiment. Accordingly, the radius R1 from the center _{O 1} of the sub bearing portion 161S to the outermost periphery of the refrigerant passage holes 136N, the refrigerant passage holes from the center _{O 1} of the sub bearing portion 161S of the rotary compressor 1 of the first embodiment shown in FIG. 4 The radius can be smaller than the radius R1 up to the outermost periphery of 136, and the diameter of the circular lower discharge chamber recess 163S4 can be reduced.

  With the configuration of the rotary compressor 1 according to the fourth embodiment described above, the bottom area of the lower discharge chamber recess 163S4 is made smaller than the bottom area of the lower discharge chamber recess 163S of the rotary compressor 1 according to the first embodiment. The volume of 163S4 can be reduced, thereby further reducing the flow rate of the refrigerant compressed by the upper cylinder 121T and discharged from the upper discharge hole 190T backflowing the refrigerant passage hole 136N and flowing into the lower end plate cover chamber 180S4. It is possible to prevent the reduction in efficiency of the rotary compressor 1.

Moreover, the radius R1 from the center _{O 1} of the sub bearing portion 161S to the outermost periphery of the refrigerant passage holes 136N, the refrigerant passage from the center _{O 1} of the sub bearing portion 161S of the rotary compressor 1 of the first embodiment shown in FIG. 4 the hole 136 Since the radius R2 of the lower end plate 160S4 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T) can be made smaller than the radius R1 up to the outermost periphery of the lower end plate of the first embodiment. 160S (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T) can be made smaller than the radius R2 (see FIG. 4), and the material cost of the compression unit 12 can be reduced.

FIG. 9 is a bottom view of the lower end plate of the rotary compressor of the fifth embodiment. As shown in FIG. 9, in the rotary compressor 1 of the fifth embodiment, the refrigerant passage hole 136M provided in the lower end plate 160S5 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T) In the rotary compressor 1 of the fourth embodiment, the refrigerant passage hole 136N is a long hole whose width is smaller than the diameter, and the cross-sectional areas are equal. The refrigerant passage hole (long hole) 136M is formed along the circumferential direction of the lower valve seat 191S. Accordingly, the radius R1 from the center _{O 1} of the sub bearing portion 161S to the outermost periphery of the refrigerant passage holes 136M, the refrigerant passage holes from the center _{O 1} of the sub bearing portion 161S of the rotary compressor 1 of the fourth embodiment shown in FIG. 8 The radius can be smaller than the radius R1 up to the outermost periphery of 136N, and the diameter of the circular lower discharge chamber recess 163S5 can be reduced.

  With the configuration of the rotary compressor 1 of the fifth embodiment described above, the bottom area of the lower discharge chamber recess 163S5 is made smaller than the bottom area of the lower discharge chamber recess 163S4 of the rotary compressor 1 of the fourth embodiment. The volume of the concave portion 163S5 can be reduced, whereby the refrigerant compressed by the upper cylinder 121T and discharged from the upper discharge hole 190T further flows back into the lower end plate cover chamber 180S5 through the refrigerant passage hole 136M. Therefore, the efficiency of the rotary compressor 1 can be prevented from being reduced.

Moreover, the radius R1 from the center _{O 1} of the sub bearing portion 161S to the outermost periphery of the refrigerant passage holes 136M, the refrigerant passage holes from the center _{O 1} of the sub bearing portion 161S of the rotary compressor 1 of the fourth embodiment shown in FIG. 8 136N The radius R2 of the lower end plate 160S5 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T) can be made smaller than the radius R1 up to the outermost periphery of the lower end plate of the fourth embodiment. 160S4 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, the upper end plate 160T) can be made smaller than the radius R2 (see FIG. 4), and the material cost of the compression unit 12 can be further reduced.

  FIG. 10 is a lower perspective view illustrating the lower end plate of the rotary compressor of the sixth embodiment. As shown in FIG. 10, in the rotary compressor 1 of the sixth embodiment, the lower discharge chamber recess 163S and the lower discharge valve housing of the lower surface of the lower end plate 160S6 (which is a contact surface with the lower end plate cover 170S of the first embodiment). In regions other than the region where the recess 164S is formed, a refrigerant introduction portion 165S6 that is an annular groove having a depth of 1 mm or less surrounding the auxiliary bearing portion 161S is formed inside the plurality of bolt holes 137. In addition, you may form the cyclic | annular groove | channel used as the refrigerant | coolant introducing | transducing part 165S6 in the upper surface of the lower end plate cover 170S instead of the lower surface of the lower end plate 160S6.

  One end of the refrigerant introduction portion 165S6 communicates with the lower discharge chamber recess 163S, and the other end communicates with the lower discharge valve accommodation recess 164S (the refrigerant introduction portion 165S6 is connected to the lower discharge chamber recess 163S or the lower discharge valve accommodation recess 164S). You may communicate with only one of them). The refrigerant introduction portion 165S6 communicates with the lower discharge chamber recess 163S or the lower discharge valve housing recess 164S, so that the high-temperature and high-pressure refrigerant discharged from the lower discharge hole 190S passes through the lower discharge chamber recess 163S or the lower discharge valve housing recess 164S. Then, it is guided to the refrigerant introduction part 165S6.

  When the high-temperature and high-pressure refrigerant is guided to the refrigerant introduction part 165S6, the lower end plate cover 170S is heated and the lower part of the compressor casing 10 of the rotary compressor 1 is started when the air conditioner is started from a state of being stopped for a long time. The liquid refrigerant 19 (see FIG. 1) staying in the chamber is heated and vaporized as soon as possible, and the liquid refrigerant 19 is sucked up instead of the lubricating oil 18 for a long time to prevent the sliding portion of the compression section 12 from being damaged. be able to. In order to reduce the amount of the refrigerant compressed in the upper cylinder 121T flowing back through the refrigerant passage hole 136, the volume of the space of the refrigerant introduction portion 165S6 is small within a range in which the heating amount necessary for vaporizing the liquid refrigerant 19 can be secured. Therefore, the depth of the refrigerant introduction part 165S6 is made shallow within a range in which a heating amount necessary for vaporizing the liquid refrigerant 19 can be secured.

  FIG. 11 is a bottom view illustrating a state in which the lower end plate and the lower end plate cover of the rotary compressor according to the seventh embodiment are overlapped. As shown in FIG. 11, in the rotary compressor 1 of the seventh embodiment, auxiliary bolts 176 (see FIG. 3) for fastening the lower end plate 160S6 of the sixth embodiment and the lower cylinder 121S to the flat bottom plate cover 170S7. Two auxiliary bolt escape holes 171S7 are provided to prevent the head from hitting the lower end plate cover 170S7. A part of the auxiliary bolt escape hole 171S7 overlaps and communicates with the refrigerant introduction part 165S6 formed in the lower end plate 160S6, and serves as a refrigerant discharge part 172S7. When the auxiliary bolt escape hole 171S7 does not overlap with the refrigerant introduction part 165S6, the lower discharge plate recess 170S7 (170S, 170S2) is separately communicated with the lower discharge chamber recess 163S, the lower discharge valve housing recess 164S, or the refrigerant introduction part 165S6. A small hole (not shown) is provided, and this small hole may be used as the refrigerant discharge portion 172S7.

  The refrigerant discharge unit 172S7 discharges the compressed refrigerant directly into the compressor housing 10 without passing through the refrigerant passage hole 136. The refrigerant discharge portion 172S7 prevents the lowering of the efficiency and noise caused by the lubricating oil 18 accumulating in the lower discharge chamber recess 163S and the lower discharge valve housing recess 164S of the lower end plate 160S6 and the lower discharge hole 190S being immersed in the lubricating oil 18. Can do. In addition, by providing the refrigerant discharge unit 172S7, the refrigerant discharged from the refrigerant discharge unit 172S7 heats the liquid refrigerant 19 (see FIG. 1) that stays in the lower portion of the compressor housing 10 while stopped for a long time. It also has the effect of promoting vaporization.

  Although the embodiments have been described above, the embodiments are not limited to the above-described contents. In addition, the above-described constituent elements include those that can be easily assumed by those skilled in the art, those that are substantially the same, and those in a so-called equivalent range. Furthermore, the above-described components can be appropriately combined. Furthermore, at least one of various omissions, substitutions, and changes of the components can be made without departing from the scope of the embodiments.

DESCRIPTION OF SYMBOLS 1 Rotary compressor 10 Compressor housing | casing 11 Motor 12 Compression part 15 Rotating shaft 18 Lubricating oil 19 Liquid refrigerant 25 Accumulator 31T Accumulator upper L-shaped pipe 31S Accumulator lower L-shaped pipe 105 Upper suction pipe 104 Lower suction pipe 107 Discharge pipe 111 Stator 112 rotor 115 clearance 121T upper cylinder 121S lower cylinder 124T upper spring hole 124S lower spring hole 125T upper piston 125S lower piston 126T upper spring 126S lower spring 127T upper vane 127S lower vane 128T upper vane groove 128S lower vane groove 130T upper cylinder chamber 130S lower Cylinder chamber 131T Upper suction chamber 131S Lower suction chamber 133T Upper compression chamber 133S Lower compression chamber 135T Upper suction hole 135S Lower suction hole 136, 136N, 136M Cold Medium passage hole 137 Bolt hole 140 Intermediate partition plate 151 Secondary shaft portion 152T Upper eccentric portion 152S Lower eccentric portion 153 Main shaft portion 155 Oil supply vertical hole 156 Oil supply horizontal hole 158 Oil supply blade 160T Upper end plate 160S, 160S2, 160S4, 160S5, 160S6 Lower end plate 161T Main bearing portion 161S Sub bearing portion 163T Upper discharge chamber recess 163S, 163S2, 163S3, 163S4, 163S5 Lower discharge chamber recess 164T Upper discharge valve storage recess 164S, 164S2, 164S3 Lower discharge valve storage recess 165S6 Refrigerant inlet 166S8 Refrigerant discharger 170T Upper end plate cover 170S, 170S2, 170S7 Lower end plate cover 171S2 Recess 171S7 Auxiliary bolt escape hole 172S7 Refrigerant discharge part 172T Upper end plate cover discharge hole 174, 175 Through bolt 176 Auxiliary bolt G 180T Upper end plate cover chamber 180S, 180S2, 180S3, 180S4, 180S5 Lower end plate cover chamber 190T Upper discharge hole 190S Lower discharge hole 191S Lower valve seat 200T Upper discharge valve 200S Lower discharge valve 201T Upper discharge valve holder 201S, 201S3 Lower discharge valve Presser 202T Upper rivet 202S Lower rivet 310 Mounting leg

Claims (9)

A vertically mounted cylindrical compressor housing that is provided with an upper suction pipe and a lower suction pipe that are provided with a discharge pipe that discharges the refrigerant at the upper part and that sucks refrigerant at the lower part of the side surface, and a side portion of the compressor case An accumulator fixed to the upper suction pipe and the lower suction pipe, a motor disposed in the compressor housing, a motor disposed in the compressor housing and disposed below the motor and driven by the motor. A compression section that sucks and compresses refrigerant from the accumulator through a pipe and a lower suction pipe and discharges the refrigerant from the discharge pipe;
The compression unit is
An annular upper cylinder and a lower cylinder;
An upper end plate closing the upper side of the upper cylinder and a lower end plate closing the lower side of the lower cylinder;
An intermediate partition plate disposed between the upper cylinder and the lower cylinder and closing the lower side of the upper cylinder and the upper side of the lower cylinder;
A rotating shaft supported by a main bearing portion provided on the upper end plate and an auxiliary bearing portion provided on the lower end plate and rotated by the motor;
An upper eccentric portion and a lower eccentric portion provided with a phase difference of 180 ° from each other on the rotating shaft;
An upper piston fitted into the upper eccentric portion and revolved along the inner peripheral surface of the upper cylinder to form an upper cylinder chamber in the upper cylinder;
A lower piston fitted into the lower eccentric part and revolving along the inner peripheral surface of the lower cylinder to form a lower cylinder chamber in the lower cylinder;
An upper vane that protrudes from the upper vane groove provided in the upper cylinder into the upper cylinder chamber and contacts the upper piston to divide the upper cylinder chamber into an upper suction chamber and an upper compression chamber;
A lower vane protruding from a lower vane groove provided in the lower cylinder into the lower cylinder chamber and contacting the lower piston to partition the lower cylinder chamber into a lower suction chamber and a lower compression chamber;
An upper end plate cover that covers the upper end plate and forms an upper end plate cover chamber between the upper end plate and has an upper end plate cover discharge hole that communicates the upper end plate cover chamber and the inside of the compressor housing;
A lower end plate cover that covers the lower end plate and forms a lower end plate cover chamber with the lower end plate;
An upper discharge hole provided in the upper end plate for communicating the upper compression chamber and the upper end plate cover chamber;
A lower discharge hole provided in the lower end plate for communicating the lower compression chamber and the lower end plate cover chamber;
A refrigerant passage hole penetrating the lower end plate, the lower cylinder, the intermediate partition plate, the upper end plate, and the upper cylinder and communicating the lower end plate cover chamber and the upper end plate cover chamber;
A rotary compressor comprising:
An upper discharge valve housing recess provided in the upper end plate and extending in a groove shape from the position of the upper discharge hole;
A lower discharge valve housing recess provided in the lower end plate and extending in a groove shape from the position of the lower discharge hole;
A reed valve type upper discharge valve whose rear end portion is fixed in the upper discharge valve housing recess by an upper rivet and whose front portion opens and closes the upper discharge hole, and a rear end portion overlaps the upper discharge valve, and the upper discharge An upper discharge valve presser that is fixed by the upper rivet in the valve housing recess and the front part is warped to regulate the opening of the upper discharge valve;
A reed valve type lower discharge valve whose rear end is fixed in the lower discharge valve housing recess by a lower rivet and whose front part opens and closes the lower discharge hole and the rear end overlaps the lower discharge valve and the lower discharge A lower discharge valve holder which is fixed by the lower rivet in the valve housing recess and the front part is warped to regulate the opening of the lower discharge valve and is housed in the lower discharge valve housing recess;
With
The lower end plate cover is formed in a flat plate shape,
A lower discharge chamber recess is formed on the lower end plate so as to overlap the lower discharge hole side of the lower discharge valve housing recess, and the lower discharge chamber recess has a center of the sub-bearing portion and the lower discharge hole. A first diameter line passing through the center and the midpoint of the line segment connecting the centers of the lower rivets, and a second diameter line opened at a pitch angle of 90 ° about the center of the auxiliary bearing portion in the direction of the lower discharge hole Is formed within the fan-shaped range between
The lower end plate cover chamber is constituted by the lower discharge chamber recess and the lower discharge valve housing recess,
The refrigerant passage hole is disposed in communication with the lower discharge chamber recess at a position on the outer peripheral side of the lower end plate with respect to the lower discharge hole and at a position inside the inner peripheral wall of the lower discharge chamber recess. A rotary compressor characterized by that.   The rotary compressor according to claim 1, wherein the refrigerant passage hole is disposed in contact with an inner peripheral wall of the lower discharge chamber recess.   The lower discharge seat has a lower valve seat that swells in an annular shape on the periphery of the lower discharge hole, and the depth of the lower discharge chamber recess to the lower valve seat is formed to be 1.5 times or less the diameter φD1 of the lower discharge hole. The rotary compressor according to claim 1, wherein the rotary compressor is provided.   The lower discharge plate has a lower valve seat that swells in an annular shape at the periphery of the lower discharge hole, and the lower end plate cover has a recess in a portion facing the front end of the lower discharge valve presser, from the recess to the lower valve seat The rotary compressor according to claim 1, wherein the depth of the rotary compressor is formed to be not more than 1.5 times the diameter φD1 of the lower discharge hole.   The front end portion of the lower discharge valve presser is formed such that the thickness of the portion adjacent to the lower end plate cover is thinner than the thickness of the other portion. The described rotary compressor.   The rotary compressor according to any one of claims 1 to 5, wherein the refrigerant passage hole includes a plurality of circular holes.   6. The rotary compressor according to claim 1, wherein the refrigerant passage hole is a long hole along a circumferential direction of the lower discharge hole.   In the lower end plate or the lower end plate cover, a refrigerant introduction portion communicating with the lower discharge chamber recess or the lower discharge valve housing recess is formed as an annular groove having a depth of 1 mm or less surrounding the auxiliary bearing portion of the lower end plate. The rotary compressor according to any one of claims 1 to 7, wherein the rotary compressor is provided.   The lower end plate cover is provided with a refrigerant discharge portion that directly communicates the lower discharge chamber recess or the lower discharge valve housing recess or the refrigerant introduction portion with the inside of the compressor case and discharges the refrigerant into the compressor case. The rotary compressor according to claim 8, wherein the rotary compressor is provided.

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