JP2011157974A - Scroll compressor and refrigerating cycle equipped with the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent a drop in the efficiency of a compressor by eliminating insufficient sealing of a compression chamber on the inner line side of a turning scroll in a horizontal scroll compressor using a pair of a fixed scroll and the turning scroll of asymmetrical tooth form. <P>SOLUTION: The scroll compressor 100 has a plurality of compression chambers 103 formed by the turning scroll 101 and the fixed scroll 102 with a scroll lap 101b. A back pressure chamber 131 is formed on the anti-lap side of the turning scroll. An oil storage chamber 133 storing oil is formed in a sealed container 122. The fixed scroll is formed with a suction dig-in 102e and a round groove 102m located on the circumferentially opposite side to a refrigerant flow direction with the suction part as a starting point. The turning scroll is formed with an opening for supplying oil to the lap side from the back pressure chamber or the oil storage part. In association with the turning motion of the turning scroll, oil is intermittently supplied to the compression chambers using the groove and the opening. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a scroll compressor and a refrigeration cycle in which the scroll compressor is mounted, and more particularly to a scroll compressor suitable for mounting in a refrigeration air conditioner or a heat pump type hot water heater and a refrigeration cycle in which the scroll compressor is mounted.

  An example of a conventional scroll compressor is described in Patent Document 1. In the scroll compressor described in this publication, the tooth shape or the wrap shape of the orbiting scroll and the fixed scroll so that the closed volumes of the compression chamber formed on the outer line side of the orbiting scroll and the compression chamber formed on the inner line side are different. (Hereinafter referred to as an asymmetric tooth profile). In such a scroll compressor having an asymmetric tooth profile, in order to improve the sealing performance of the compression chamber, the compression chamber on the outer line side of the orbiting scroll whose pressure is higher than the pressure chamber formed on the inner line side of the orbiting scroll is completely closed. Refueling for sealing has begun after reaching the state.

JP 2003-172276 A

  In the scroll compressor described in Patent Document 1, since the asymmetric tooth profile is adopted, the pressure distribution between the compression chambers is different between the outer line side compression chamber and the inner line side compression chamber of the orbiting scroll. That is, since the outer line side compression chamber having a large confined volume always starts to be compressed first, the pressure in the outer line side compression chamber is higher than the suction pressure when the inner line side compression chamber starts compression. As a result, in the gap formed between the spiral bodies (wraps) of the orbiting scroll and the fixed scroll and the end plate of the mating scroll member, a leakage flow from the outer line side compression chamber to the inner line side compression chamber, which is high pressure, occurs.

Therefore, in order to improve the sealing performance on the inner line side, the lubricating oil supply path is determined so that the leakage flow from the outer line side includes the lubricating oil. However, under operating conditions where the pressure difference between the suction pressure and the discharge pressure is large, or under high driving conditions using CO ₂ as the refrigerant, only the lubricating oil that leaks from the gap formed between the spiral body and the end plate is the lubricating oil. There is a risk that the amount of the lubricating oil for sealing the gap formed between the side surfaces of each scroll wrap is insufficient. Thereby, there exists a possibility of causing the efficiency fall of a compressor.

The present invention has been made in view of the above problems of the prior art, and its purpose is to provide a scroll compressor even when the pressure difference between the suction pressure and the discharge pressure is large or when CO ₂ is used as the refrigerant. The goal is to enable high-efficiency operation. Another object of the present invention is to eliminate a lack of seal in the compression chamber on the inner side of the orbiting scroll and prevent a reduction in the efficiency of the compressor in the horizontal scroll compressor using the fixed scroll and the orbiting scroll pair having an asymmetric tooth profile. There is to do.

  In order to achieve the above-mentioned object, the present invention forms a plurality of compression chambers by the orbiting scroll having the spiral wrap and the fixed scroll, forms a back pressure chamber on the side opposite to the orbiting scroll, and In a hermetic scroll compressor housed in a hermetic container, an oil storage chamber for storing oil is formed in the hermetic container, and a suction part is formed in the fixed scroll, and this suction part is a starting point and is located on the opposite side to the refrigerant flow direction. A groove is formed, an opening for supplying oil from the back pressure chamber or the oil storage part to the lap side is formed in the orbiting scroll, and oil is intermittently supplied to the compression chamber along with the orbiting movement of the orbiting scroll using the groove and the opening. Is.

  And preferably, the closed volume of the outer line side compression chamber formed on the outer line side of the orbiting scroll has an asymmetric tooth profile larger than the closed volume of the inner line side compression chamber formed on the inner line side, and the opening and Position where the groove overlaps at least partially while the outer line side compression chamber of the orbiting scroll is completely closed by the turning of the orbiting scroll, and does not overlap in other states Is formed.

  In order to achieve the above object, according to the present invention, the orbiting scroll, the fixed scroll meshing with the orbiting scroll, a plurality of compression chambers formed by meshing the orbiting scroll and the fixed scroll, and the fixed scroll are fixed. A scroll having a frame, a orbiting scroll, a fixed scroll, and a back pressure chamber formed by the frame, interposing a back pressure control valve between the back pressure chamber and the outer line side compression chamber, and housing each component in a sealed container. In the compressor, an oil storage chamber is formed in a hermetically sealed container, and among the plurality of compression chambers, the closed volume of the outer line side compression chamber formed on the outer line side of the orbiting scroll is an inner line side compression chamber formed on the inner line side. A compression chamber oil supply path for supplying oil from the back pressure chamber or oil storage chamber to the orbiting scroll and the fixed scroll, and this compression chamber oil supply. The road communicates with the suction part in the fixed scroll, and in the orbiting scroll, at least one of the period from the state where the outer line side compression chamber is completely closed to the state where the inner line side compression chamber is completely closed due to the turning of the orbiting scroll. At this time, it is formed at a position communicating with the compression chamber oil supply path formed in the fixed scroll.

  In addition, it is desirable to mount the scroll compressor capable of using carbon dioxide as a refrigerant in a refrigeration cycle for a heat pump water heater. Further, the scroll compressor preferably uses carbon dioxide as a working refrigerant and uses at least one of polyalkylene glycol oil, polyol ester oil, polyalphaolefin oil, paraffinic mineral oil, and naphthenic mineral oil as refrigeration oil.

According to the present invention, the scroll compressor can be operated with high efficiency even when the pressure difference between the suction pressure and the discharge pressure is large or when CO ₂ is used as the refrigerant. Is possible. Further, in the horizontal scroll compressor using the fixed scroll and the orbiting scroll pair having an asymmetric tooth profile, the lack of seal of the compression chamber on the inner side of the orbiting scroll is eliminated, and the efficiency of the compressor is prevented from being lowered.

The longitudinal cross-sectional view of one Example of the horizontal scroll compressor which concerns on this invention. AA arrow sectional drawing of FIG. The detailed longitudinal cross-sectional view of the differential pressure control valve which the scroll compressor shown in FIG. 1 has. The figure seen from the lap side of the turning scroll used for the scroll compressor shown in FIG. BB 'arrow sectional drawing of FIG. The figure explaining compression operation by scroll wrap. The figure which looked at the fixed scroll used for other Examples of the horizontal scroll compressor concerning the present invention from the lap side. CC 'arrow sectional drawing of FIG. The figure which looked at the turning scroll used with the fixed scroll shown in FIG. 7 from the scroll wrap side. The figure explaining compression operation by scroll wrap.

  Hereinafter, an embodiment of a horizontal scroll compressor 100 according to the present invention will be described with reference to the drawings. FIG. 1 is a longitudinal sectional view of a horizontal scroll compressor 100. In FIG. 1, each part of the orbiting scroll 101, the fixed scroll 102, the frame 109, and the Oldham ring 110 included in the horizontal scroll compressor 100 is shown in cross sections at different positions in the circumferential direction. 2 is a cross-sectional view taken along the line AA in FIG. 1 and is a view of the fixed scroll 102 as viewed from the scroll wrap 102r side. FIG. 3 is a detailed cross-sectional view of the differential pressure control valve provided in the horizontal scroll compressor 100. FIG. 4 is an axial view of the orbiting scroll 101 as viewed from the scroll wrap 101b side. 5 is a cross-sectional view taken along line BB in FIG. FIG. 6 is a diagram for explaining the compression operation of the compression chamber 103 formed by the orbiting scroll 101 and the fixed scroll 102.

  In the horizontal scroll compressor 100, a compressor element and a motor 112 are accommodated in a hermetic container 122 including a cylindrical portion formed in a cylindrical shape and an end plate formed in an end plate shape that covers both side portions of the cylindrical portion. ing. The compressor element has an orbiting scroll 101 and a fixed scroll 102 that forms a compression chamber 103 together with the orbiting scroll.

  In the orbiting scroll 101, a scroll wrap 101b formed in a spiral shape is erected on a flat end plate 101a. On the back side of the end plate 101a, a ring-shaped bearing holding portion 101d for holding the orbiting bearing 101c and an orbiting Oldham groove 101e are provided so that the orbiting scroll 101 can rotate (turn) eccentrically from the axis of the rotating shaft 111. It has been.

  A release valve plate 104, which is a reed valve plate, is provided on the surface of the fixed scroll 102 on the side opposite to the fixed scroll wrap so as to cover a release hole 102c described in detail later. A retainer 104 a that overlaps the release valve plate 104 and restricts the opening degree of the release valve plate 104 is disposed, and one end side of the release valve plate 104 and the retainer 104 a is fixed by a fixing screw 105. A discharge hole 102 d is opened at the center of the fixed scroll 102.

  In the fixed scroll 102, as shown in FIG. 2, a fixed scroll wrap 102r is formed in a spiral shape by cutting the fixed scroll reference surface 102a as an end surface. Therefore, the end surface (tooth surface) of the fixed scroll wrap 102r is on the same plane as the fixed scroll reference surface 102a. A peripheral groove 102b is formed in a ring shape on the outer peripheral side of the fixed scroll wrap 102r. A plurality of notches are formed in the outer peripheral portion of the fixed scroll 102, and the notches act as a plurality of flow grooves 102g through which discharge gas and oil flow.

  A total of four release holes 102c are formed at the root of the root of the fixed scroll wrap 102r in proximity to the fixed scroll wrap 102r. The release hole 102 c penetrates the fixed scroll 102 in the axial direction. The reason for providing the release hole 102c is to discharge the refrigerant gas from the release hole 102c when the pressure in the compression chamber 103 becomes equal to or higher than the discharge pressure.

  A suction portion 102s is formed on the outer diameter side of the bottom surface of the fixed scroll 102 where the fixed scroll wrap 102r ends. A suction hole 102f is formed from the anti-fixed scroll wrap side so as to partially overlap the suction portion 102s. A suction dig 102e whose depth gradually changes is formed along the fixed scroll wrap 102r from the suction portion 102s. A suction pipe 106 is inserted into the suction hole 102f from the anti-fixed scroll wrap side. An R-groove 102m having a constant radius is formed continuously to the suction dig 102e on the opposite side of the suction dig 102e across the suction portion 102s. The R groove 102m is formed by a predetermined angle range in the circumferential direction.

  Here, as shown in FIG. 1, when the suction pipe 106 is inserted into the suction hole 102f, a valve body 107a for sealing the suction hole 102f and a check valve spring 107b for pressing the valve body 107a are provided. Insert into the suction hole 102f. The valve body 107 a and the check valve spring 107 b form a suction side check valve 107.

  A differential pressure control valve 108 is provided in a peripheral groove 102b portion of the fixed scroll 102 at a position away from the position where the R groove 102m is formed. Specifically, as shown in FIGS. 2 and 3, a stepped hole (valve hole) 102 h with a diameter decreasing in order is formed from the anti-fixed scroll wrap side of the fixed scroll 102.

  The valve hole 102h is a three-stage hole, and a valve body 108a having a shape in which a cylinder is attached to the center portion of the seat is held at the boundary between the small diameter portion and the intermediate diameter portion. The step surface between the small diameter portion and the intermediate diameter portion forms a valve seal surface 102i. A differential pressure valve spring 108b that presses the valve body 108a is inserted into the intermediate diameter portion. The large-diameter portion is fitted with a valve cap 108d, which is inserted into the differential pressure valve spring 108b and has a projection 108c formed at the center thereof for holding the differential pressure valve spring 108b, with the valve cap insertion portion 102n as a guide. In the differential pressure control valve 108 configured as described above, the valve body 108a and the differential pressure valve spring 108b are inserted into the intermediate diameter portion of the valve hole 102h, one end of the differential pressure valve spring 108b is inserted into the protrusion 108c, and the valve cap 108d is connected to the valve cap 108d. It press-fits into the valve cap insertion part 102n having a larger diameter than the intermediate diameter part of the hole 102h.

  A compression chamber conduction path 102k is formed obliquely from the side of the intermediate diameter portion of the valve hole 102h toward the tooth bottom of the fixed scroll 102. The compression chamber conduction path 102k communicates with the compression chamber 103 (see FIG. 4) formed by the fixed scroll inner line 102j and the orbiting scroll outer line 101f.

  Returning to FIG. 1, a frame 109 that covers the anti-scroll wrap side (rear side) of the orbiting scroll 101 and the outer diameter side of the orbiting scroll 101 and is bolted to the fixed scroll 102 is disposed facing the fixed scroll 102. Yes. In the frame 109, a fixed attachment surface 109a for attaching the fixed scroll 102 to the outer peripheral portion is formed. A swivel pinching surface 109b is provided inside the fixed mounting surface 109a.

  A frame Oldham groove 109c is provided on the inner side of the turning and sandwiching surface 109b. The frame Oldham groove 109 c is provided in order to dispose the Oldham ring 110 for rotating the orbiting scroll 101 between the frame 109 and the orbiting scroll 101. In the Oldham ring 110, a frame protrusion 110a is formed on the surface of the Oldham ring 110 facing the frame 109, and a swiveling protrusion 110b is formed on the opposite surface.

  A shaft through hole is formed at the center of the frame 109, and a shaft seal 109d and a main bearing 109e are held side by side in the shaft through hole. A center portion of the frame 109 that faces the end surface of the orbiting scroll 101 is a shaft thrust surface 109f, which is a surface that supports the axial force from the shaft 111. On the outer peripheral surface of the frame 109, a plurality of flow grooves 109h serving as refrigerant gas and oil passages are formed.

  The shaft 111 having the eccentric portion 111e is supported by a turning bearing 101c having one end held by a turning scroll, and an intermediate portion is supported by a main bearing 109e. The shaft 111 extends right and left in the sealed container 122. A shaft oil supply hole 111a that penetrates the shaft center portion of the shaft 111 to the left and right is formed, and a plurality of radial holes communicating with the shaft oil supply hole 111a are provided. These radial holes are a main bearing oil supply hole 111b, a shaft seal oil supply hole 111c, and a sub-bearing oil supply hole 111d in this order from the orbiting scroll 101 side.

  An eccentric portion 111 e that is one end side of the shaft 111 is fitted to the orbiting bearing 101 c held by the orbiting scroll 101. The other end of the shaft 111 is fitted to the auxiliary bearing 113. The auxiliary bearing 113 is held by the auxiliary bearing housing 115. The auxiliary bearing housing 115 is fixed to the auxiliary bearing support plate 114 fixed to the hermetic container 122. A rotor 112 a constituting the motor 112 is press-fitted between the positions corresponding to the sub bearing 113 and the frame 109, which is an intermediate portion of the shaft 111. The stator 112b of the motor 112 is shrink-fitted in the sealed container 122.

  The operation of the horizontal scroll compressor 100 configured as described above will be described below. When the rotor 112a of the motor 112 rotates, the shaft 111 to which the rotor 112a is attached rotates, and the orbiting scroll 101 attached to the end of the shaft 111 performs the orbiting motion. Since the Oldham ring 110 is provided, the orbiting scroll 101 is prevented from rotating.

  When the turning scroll 101 turns, the refrigerant gas guided to the suction hole 102f through the suction pipe 106 flows into the compression chamber 103 formed between the turning and fixed scrolls 101 and 102. Then, the refrigerant gas is compressed in the compression chamber 103 and discharged from the discharge hole 102d to the fixed back chamber 117 formed between the end plate portion of the sealed container 122 and the anti-fixed scroll wrap side of the fixed scroll 102.

  The refrigerant gas discharged into the fixed back chamber 117 flows into the motor chamber 118 containing the rotor 112a of the motor 112 through the fixed scroll 102 and the flow grooves 102g and 109h formed in the outer peripheral portion of the frame. The refrigerant gas that has entered the motor chamber 118 passes between the rotor 112a and the stator 112b of the motor 112. In the process, the refrigerant gas collides with the rotor 112a and the stator 112b, and the lubricating oil contained in the refrigerant gas is separated. The separated lubricating oil falls to the lower part of the motor chamber 118.

  The refrigerant gas that has flowed into the motor chamber 118 passes through a vent hole 114 a formed in the auxiliary bearing support plate 114. The refrigerant gas that has passed through the vent hole 114 a collides with an oil separation plate 125 that is disposed on the right side of the right end portion of the shaft 111 and that partitions the sealed container 122. The refrigerant gas that has collided with the oil separation plate 125 separates the lubricating oil contained in the refrigerant gas at the time of the collision, and flows out from the discharge pipe 120 attached to the end plate portion of the hermetic container 122.

  An oil storage chamber 121 for storing lubricating oil is formed in a lower portion of the space between the end plate on the right end side of the sealed container 122 and the oil separation plate 125. The pressure in the oil storage chamber 121 is lower than the pressure in the motor chamber 118 due to the flow resistance of the refrigerant gas passing through the vent hole 114a. As a result, the lubricating oil 119 in the motor chamber 118 is pushed out to the oil storage chamber 121 side from the oil guide hole 114d formed in the lower part of the sub-bearing support plate 114 whose central portion is convexly formed on the motor 112 side. The oil level of the oil storage chamber 121 is higher than the oil level of the motor chamber 118.

  The manner in which the lubricating oil stored in the oil storage chamber 121 is supplied to each part in the sealed container 122 will be described below. On the back side of the orbiting scroll 101, an intermediate pressure chamber 123 is formed by the orbiting scroll 101, the fixed scroll 102, and the frame 109. The pressure in the intermediate pressure chamber 123 is maintained at a pressure between the suction pressure and the discharge pressure (hereinafter referred to as an intermediate pressure) by the differential pressure control valve 108.

  Since the lubricating oil 119 in the oil storage chamber 121 is in a discharge pressure atmosphere, a differential pressure between the discharge pressure and the intermediate pressure is generated between the intermediate pressure chamber 123 and the lubricating oil 119 in the oil storage chamber 121. Due to this differential pressure, oil is supplied from the oil supply pipe 124 to the rotary bearing 101c through the shaft oil supply hole 111a. Further, when the shaft 111 rotates, a centrifugal force is generated, and the lubricating oil flowing through the shaft oil supply hole 111 a penetrating the shaft center portion of the shaft 111 is separated from the main bearing oil supply hole 111 b formed in the radial direction of the shaft 111 and the shaft seal. Oil is supplied to each sliding portion from the oil supply hole 111c and the auxiliary bearing oil supply hole 111d. The lubricating oil 119 supplied to the slewing bearing 101 c leaks into the intermediate pressure chamber 123. Then, it enters the compression chamber conduction path 102k from the differential pressure control valve 108 and is discharged into the fixed back chamber 117 together with the refrigerant gas.

  4 is a top view of the orbiting scroll, and FIG. 5 is a cross-sectional view taken along the line BB ′ of FIG. As can be seen from these drawings, an oil pocket 126 that is a depression is formed in the end plate 101 a of the orbiting scroll 101. As described above, the fixed scroll 102 is formed with the R groove 102m, and the R groove 102m has a suction pressure. The oil pocket 126 and the R groove 102m form an oil supply path to the extension-side compression chamber of the orbiting scroll 101 as shown in FIG.

  The operation of the oil pocket 126 will be described with reference to FIG. FIG. 6 is a diagram showing how the compression chamber 103 formed by the scroll wrap 101 b of the orbiting scroll 101 and the fixed scroll wrap 102 a of the fixed scroll 102 changes as the shaft 111 rotates.

  FIG. 5A shows the angle of the eccentric portion 111e of the shaft 111 at the reference position, and this angle is referred to as a crank angle of 0 °. FIG. 6B shows the angle of the eccentric portion 111e of the shaft 111 advanced by 125 °, and FIG. 5C shows the angle of the eccentric portion 111e of the shaft 111 advanced by 180 °. FIG. 4D shows a state where the angle of the eccentric portion 1111e of the shaft 111 has advanced to 270 °.

  The crank angle 0 ° shown in FIG. 5A corresponds to the case where the outer line side of the orbiting scroll 101 has completed suction. In the rotation section of the shaft 111 from the crank angle 0 ° to the crank angle 125 ° shown in FIG. 5B, the oil pocket 126 communicates with the suction portion 102s that is the suction pressure through the R groove 102m. Yes. At this time, the lubricating oil flows in the R groove 102 as indicated by an arrow in FIG. When the rotation angle of the shaft 111 is in the range of 0 ° to 125 °, refueling for sealing the compression chamber 103a formed on the inner line side of the orbiting scroll 101 is completed.

  As shown in FIG. 6C and FIG. 6D, when the orbiting scroll 101 orbits and the oil pocket 126 communicates with the peripheral groove 102b of the fixed scroll 102 shown hatched, the oil pocket 126 is supplied with oil. Is done. Since the peripheral groove 102b communicates with the intermediate pressure chamber 123, the pressure of the peripheral groove 102b becomes an intermediate pressure.

  When the refrigerant gas has been sucked into the space that will be the future compression chamber 103 b formed on the outer line side of the orbiting scroll 101, the oil is supplied to the outer compression chamber 103 b of the orbiting scroll 101 via the differential pressure control valve 108. In the case of a scroll wrap having an asymmetric tooth profile, the pressure in the compression chambers 103a and 103b is different from the conventional symmetrical tooth profile, and the pressure in the compression chamber 103b on the outer line side of the orbiting scroll 101 which starts the compression operation first is the inner line side. It is higher than the compression chamber 103a.

  Therefore, the oil supplied to the compression chamber 103b on the outer line side of the orbiting scroll 101 is extended through the tooth bottoms of the scroll wraps 101b and 102r as the pressure of the compression chamber 103b is increased by the rotation of the shaft 111. The lubricating oil that seals the compression chamber 103a on the extension side is insufficient only by the conventional method of flowing into the compression chamber 103a on the side. Therefore, in this embodiment, the oil pocket 126 and the R groove 102m are used to ensure the oil supply to the compression chamber 103a on the extension line side. The lubricating oil supplied from the oil pocket 126 can seal not only the tooth bottoms of the fixed scroll wrap 102a and the orbiting scroll wrap 101b but also the gap formed between the side surfaces of the scroll wraps 101b and 102r. is there.

  In particular, the gap between the tooth tips of the scroll wraps 101b and 102r and the end plate is a small gap of several μm, while the side gap is several tens of μm in consideration of thermal deformation and contact prevention of the scroll wraps 101b and 102r. . Therefore, the effect of the present embodiment is remarkable under operating conditions where the pressure difference between the suction pressure and the discharge pressure is large.

According to the present embodiment, since the leakage loss of the scroll compressor can be suppressed, the efficiency of the scroll compressor is improved. This improves the system COP of the refrigeration cycle. In particular, when a CO ₂ refrigerant is used as the refrigerant, the pressure difference between the compression chambers increases because of the high pressure refrigerant and the high adiabatic index, but according to this embodiment, the compression chamber is reliably sealed. This can greatly improve the efficiency of the scroll compressor.

  In the above-described embodiment, the section in which the oil pocket 126 communicates with the suction pressure is defined as the section of 0 ° to 125 ° with the crank angle when the outer line side of the orbiting scroll 101 has completed the suction being set to 0 °. The end point of the section may be any crank angle from 0 ° to approximately 180 °. Further, although the oil pocket 126 has a circular recess, it may have any shape as long as it achieves the object of the present invention.

  Another embodiment of the horizontal scroll compressor 100 according to the present invention will be described with reference to FIGS. 7 is a view corresponding to FIG. 2, FIG. 8 is a view corresponding to FIG. 5, and is a cross-sectional view taken along the line CC 'of FIG. FIG. 9 is a view corresponding to FIG. 4, and FIG. 10 is a view showing a change in the compression chamber 103 formed by the scroll wraps 101 b and 102 r of the orbiting scroll 101 and the fixed scroll 102.

  In the present embodiment, the oil supply path to the compression chamber 103a on the inner line side of the orbiting scroll 101 constituted by the oil pocket 126 and the R groove 102m is different from the above embodiment. That is, in the above embodiment, the pressure of the lubricating oil supplied from the oil pocket 126 changes from the intermediate pressure of the peripheral groove 102b provided in the fixed scroll 102 to the suction pressure of the R groove 102m. In this embodiment, since the peripheral groove 102b is not provided, the pressure changes from the discharge pressure of the oil storage passage 102p communicating with the oil storage chamber 121 to the suction pressure of the R groove 102m.

  As in the embodiment shown in FIG. 6, the section in which the oil pocket 126 communicates with the suction pressure is 0 ° to 125 ° with the crank angle when the suction of the outer line side of the orbiting scroll 101 is completed as 0 °. The range of this communication section can be changed as in the above embodiment. According to the present embodiment, since the oil is supplied at the discharge pressure of the compressor, the flow path resistance is large and the oil can be supplied more reliably than in the above embodiment.

  In the above embodiments, carbon dioxide is used as the working refrigerant. However, the refrigerant may be a refrigerant that is normally used in an air conditioner. When carbon dioxide is used as the working refrigerant, it is preferable to use at least one of polyalkylene glycol oil, polyol ester oil, polyalphaolefin oil, paraffinic mineral oil, and naphthenic mineral oil as the refrigerator oil.

101 orbiting scroll 101a end plate 101b scroll wrap 101c orbiting bearing 101d bearing holding part 101e orbiting Oldham groove 101f orbiting scroll outer line 101g orbiting scroll inner line 102 fixed scroll 102a fixed scroll reference surface 102b peripheral groove 102c release hole 102d discharge hole 102e suction indentation 102f suction Hole 102g, 109h Flow groove 102h Valve hole 102i Valve seal surface 102j Fixed scroll extension 102k Compression chamber conduction path 102m R groove 102n Valve cap insertion part 102p Oil storage conduction path 102r Fixed scroll wrap 103 Compression chamber 104 Release valve plate 104a Retainer 105 Fixing screw 106 Suction pipe 107 Suction side check valves 107a, 108a Valve body 107b Check valve spring 108 Differential pressure control valve 108b Differential pressure valve spring 108 c Protrusion 108d Valve cap 109 Frame 109a Fixed mounting surface 109b Swivel pinching surface 109c Frame Oldham groove 109d Shaft seal 109e Main bearing 109f Shaft thrust surface 110 Oldham ring 110a Frame projection 110b Swivel projection 111 Shaft 111a Shaft oiling hole 111b Main bearing oiling Hole 111c Shaft seal oil supply hole 111d Sub bearing oil supply hole 111e Eccentric part 112 Motor 112a Rotor 112b Stator 113 Sub bearing 114 Sub bearing support plate 114a Vent hole 114d Oil guide hole 115 Sub bearing housing 116 Suction port 117 Fixed back chamber 118 Motor chamber 119 Lubricating oil 120 Discharge pipe 121 Oil storage chamber 122 Sealed container 123 Intermediate pressure chamber 124 Oil supply pipe 125 Oil separation plate 126 Oil pocket

Claims (6)

  A swivel scroll having a spiral wrap and a fixed scroll form a plurality of compression chambers, a back pressure chamber is formed on the opposite side of the orbiting scroll, and the sealed scroll and the fixed scroll are housed in a sealed container. In the scroll compressor, an oil storage chamber for storing oil is formed in the sealed container, a suction portion is formed in the fixed scroll, and a groove located on the opposite side to the refrigerant flow direction from the suction portion is formed as a starting point. An opening for supplying oil to the lap side from the back pressure chamber or the oil storage part is formed in the orbiting scroll, and the groove and the opening are used to intermittently supply oil to the compression chamber along with the orbiting movement of the orbiting scroll. A featured scroll compressor.   The closed volume of the outer line side compression chamber formed on the outer line side of the orbiting scroll has an asymmetric tooth profile larger than the closed volume of the inner line side compression chamber formed on the inner line side. The scroll compressor described.   The opening and the groove overlap at least partly while the outer line side compression chamber of the orbiting scroll changes from the closed state to the closed state by the orbiting movement of the orbiting scroll, The scroll compressor according to claim 2, wherein the scroll compressor is formed at a position that does not overlap in the state.   A orbiting scroll, a fixed scroll meshing with the orbiting scroll, a plurality of compression chambers formed by meshing the orbiting scroll and the fixed scroll, a frame to which the fixed scroll is fixed, the orbiting scroll and the fixed scroll, A scroll compressor including a back pressure chamber formed by a frame, interposing a back pressure control valve between the back pressure chamber and the outer line side compression chamber, and housing each of the components in a sealed container. An oil storage chamber is formed in the container, and, among the plurality of compression chambers, the closed volume of the outer line side compression chamber formed on the outer line side of the orbiting scroll is confined to the inner line side compression chamber formed on the inner line side. A compression chamber oil supply path for supplying oil from the back pressure chamber or the oil storage chamber to the orbiting scroll and the fixed scroll. This compression chamber oil supply path communicates with the suction part in the fixed scroll, and in the orbiting scroll, the outer line side compression chamber is completely closed by the turning of the orbiting scroll until the inner line side compression chamber is completely closed. A scroll compressor characterized in that it is formed at a position communicating with a compression chamber oil supply path formed in the fixed scroll at least at any time of the above.   A refrigeration cycle for a heat pump water heater, wherein carbon dioxide can be used as a refrigerant and the scroll compressor according to claim 3 is mounted.   The scroll compression according to claim 4 or 5, wherein carbon dioxide is used as a working refrigerant, and at least one of polyalkylene glycol oil, polyol ester oil, polyalphaolefin oil, paraffinic mineral oil, and naphthenic mineral oil is used as refrigerator oil. Refrigeration cycle equipped with a machine.

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