JP2017172346A - Scroll compressor and air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce heating loss and re-expansion loss in a suction chamber.SOLUTION: A scroll compressor S includes a fixed scroll 12 having an end plate 12b and a spiral lap 12a vertically disposed on the end plate, a revolving scroll 11 having an end plate 11b and a spiral lap 11a disposed on the end plate, and forming a compression chamber 51 for compressing a refrigerant, with the fixed scroll, and a suction chamber 4 for supplying the refrigerant to the compression chamber. The end plate of the revolving scroll is provided with an oil pumping portion alternately connected to the inside of a compression chamber-side space and the inside of a suction chamber-side space partitioned by the lap of the fixed scroll in accompany with revolving motion of the revolving scroll.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a scroll compressor and an air conditioner including the same.

  For example, a scroll compressor is used as an apparatus for compressing a gaseous refrigerant in an air conditioner. A scroll compressor is a device that compresses a working fluid such as a refrigerant using a fixedly installed scroll (hereinafter referred to as “fixed scroll”) and a scroll that performs a revolving motion (hereinafter referred to as “revolving scroll”). is there.

The scroll compressor includes a suction chamber, a back pressure chamber, and a compression chamber.
The suction chamber is a room for temporarily storing the refrigerant sucked from the outside and supplying it to the compression chamber.
The back pressure chamber is a chamber for applying a back pressure in the direction from the orbiting scroll side to the fixed scroll side to the refrigerant. The scroll compressor presses the orbiting scroll toward the fixed scroll with the refrigerant that has given back pressure so that the orbiting scroll does not leave the fixed scroll.
The compression chamber is a chamber for compressing the refrigerant. The scroll compressor rotates the orbiting scroll in a state in which the spiral wrap formed on the fixed scroll and the spiral wrap formed on the orbiting scroll are meshed with each other, so that the fixed scroll wrap and the orbiting scroll wrap are rotated. The compression chamber is formed between the two. The refrigerant compressed in the compression chamber is discharged from the discharge port to the outside of the compression chamber, and sent to a heat exchanger or the like provided outside the scroll compressor.

  Between the suction chamber and the compression chamber, a flow path (hereinafter referred to as “refrigerant flow path”) for supplying the refrigerant to the compression chamber is formed. Further, a flow path (hereinafter referred to as “back pressure chamber oil outflow path”) for supplying lubricating oil to the compression chamber is formed between the back pressure chamber and the compression chamber. The opening that faces the compression chamber of the back pressure chamber oil outflow passage functions as an oil introduction portion that introduces lubricating oil into the compression chamber. One end of the back pressure chamber oil outflow passage is connected to the back pressure chamber, and the other end is connected to an intermediate portion of the refrigerant flow path. A back pressure adjusting mechanism for adjusting the back pressure is provided in the middle part of the back pressure chamber oil outflow passage.

  The scroll compressor supplies lubricating oil to the back pressure chamber and feeds the lubricating oil into the compression chamber through the back pressure chamber oil outflow passage. However, in the scroll compressor, since the back pressure chamber oil outflow path is connected to the middle portion of the refrigerant flow path, the front end portion of each scroll wrap is formed in the space from the suction chamber to the oil introduction section in the refrigerant flow path. And the amount of oil required to seal the sides tends to be insufficient. As a result, the scroll device may cause refrigerant leakage loss. In particular, when the scroll compressor has a differential pressure oil supply mechanism, refrigerant leakage loss is likely to occur under low differential pressure operating conditions, and compression efficiency is thereby liable to decrease.

Therefore, an oil pumping part is formed in the orbiting scroll as an oil supply path different from the back pressure chamber oil outflow path, and the lubricating oil in the back pressure chamber is supplied to the suction chamber using the orbiting scroll's orbiting motion. A scroll compressor has been proposed (see, for example, Patent Document 1).
According to this scroll compressor, since lubricating oil can be supplied to the suction chamber, for example, in a space where there is a shortage of oil from the suction chamber to the oil introduction portion in the refrigerant flow path, there is a shortage of oil. Can be resolved.

JP 2011-157974 A

  However, the conventional scroll compressor described in Patent Document 1 has a problem that heating loss and re-expansion loss may be caused in the suction chamber as described below.

  For example, in a conventional scroll compressor, in order to supply the lubricating oil in the back pressure chamber to the suction chamber, the lubricating oil in a higher temperature and high pressure state is caused to flow into the suction chamber than the refrigerant in the suction chamber. Such a conventional scroll compressor raises the temperature of the refrigerant by bringing the refrigerant into contact with high-temperature and high-pressure lubricating oil in the suction chamber, and as a result, heat loss (of the volumetric efficiency of the refrigerant) occurs in the suction chamber. Decrease). Further, in the conventional scroll compressor, the lubricating oil and the refrigerant expand in the suction chamber, and as a result, the pressure in the suction chamber is increased and the re-expansion loss (of the refrigerant supplied to the suction chamber is increased). Decrease in supply amount).

  The present invention has been made in order to solve the above-described problems, and sufficiently supplies an amount of oil necessary for sealing the tip and side surfaces of each scroll wrap in a space where oil tends to be insufficient. However, a main object is to provide a scroll compressor that reduces heating loss and re-expansion loss in the suction chamber, and an air conditioner including the scroll compressor.

In order to achieve the above object, the present invention includes a fixed scroll having an end plate and a spiral wrap standing on the end plate, an end plate and a spiral wrap standing on the end plate, and the fixed scroll. An orbiting scroll that forms a compression chamber for compressing the refrigerant therebetween, and a suction chamber that supplies the refrigerant to the compression chamber. The end plate of the orbiting scroll is fixed with the orbiting motion of the orbiting scroll. A scroll compressor characterized in that an oil pumping portion communicating alternately with the inside of the space on the compression chamber side partitioned by the wrap of the scroll and the inside of the space on the suction chamber side is formed, and Provide an air conditioner.
Other means will be described later.

  The scroll compressor and the air conditioner equipped with the scroll compressor suck in the oil in the compression chamber at a lower temperature and low pressure than the oil in the back pressure chamber in order to supply the oil introduced into the compression chamber to the space on the suction chamber side. Supply to the room. Thereby, this scroll compressor and an air conditioner provided with the same can reduce heating loss and re-expansion loss in the suction chamber. In addition, this scroll compressor can sufficiently supply an amount of oil necessary for sealing the tip and side surfaces of each scroll wrap in a space where oil tends to be insufficient.

  According to the present invention, heat loss and re-expansion in the suction chamber are sufficiently supplied while supplying a sufficient amount of oil necessary to seal the tip and side surfaces of each scroll wrap in a space where oil tends to be insufficient. Loss can be reduced.

It is composition explanatory drawing of the air conditioner concerning 1st Embodiment. It is sectional drawing of the scroll compressor which concerns on 1st Embodiment. It is sectional drawing of the fixed scroll and turning scroll of the scroll compressor which concerns on 1st Embodiment seen from the lower side. It is a back pressure control mechanism in a scroll compressor concerning a 1st embodiment, and a partial expanded sectional view of the circumference. It is a block diagram of the turning scroll used for the scroll compressor which concerns on 1st Embodiment seen from the lower side. It is sectional drawing of the turning scroll used for the scroll compressor which concerns on 1st Embodiment seen from the side surface side. It is explanatory drawing of operation | movement of the scroll compressor which concerns on 1st Embodiment. It is sectional drawing of the fixed scroll and turning scroll of the scroll compressor which concern on 2nd Embodiment seen from the lower side. It is sectional drawing of the fixed scroll and turning scroll of the scroll compressor which concerns on 3rd Embodiment seen from the lower side. It is sectional drawing of the fixed scroll and turning scroll of the scroll compressor which concerns on 4th Embodiment seen from the lower side.

  Hereinafter, an embodiment of the present invention (hereinafter referred to as “the present embodiment”) will be described in detail with reference to the drawings. Each figure is only schematically shown so that the present invention can be fully understood. Therefore, the present invention is not limited to the illustrated example. Moreover, in each figure, the same code | symbol is attached | subjected about the common component and the same component, and those overlapping description is abbreviate | omitted.

[First Embodiment]
As will be described later, the scroll compressor S according to the first embodiment lubricates from the space on the compression chamber 51 side to the space on the suction chamber 4 side with an oil pumping portion 11d formed on the turning end plate 11b of the orbiting scroll 11. It has a structure for supplying oil (see FIG. 3). Hereinafter, first, the overall configuration of the air conditioner 101 including the scroll compressor S according to the first embodiment will be described, and then the configuration of the scroll compressor S will be described.

<Configuration of air conditioner>
Hereinafter, the configuration of the air conditioner 101 according to the first embodiment will be described with reference to FIG. FIG. 1 is a configuration explanatory diagram of the air conditioner 101.

  As shown in FIG. 1, the air conditioner 101 includes a scroll compressor S, a four-way valve 102, a cooling / heating throttle device 103 such as an expander, an indoor heat exchanger 104, and an outdoor heat exchanger 105. These are configured to be annularly connected by a predetermined pipe 106.

  In the first embodiment, the air conditioner 101 will be described as a heat pump type device. The air conditioner 101 can perform a cooling operation and a heating operation by switching the four-way valve 102. The air conditioner 101 uses the indoor heat exchanger 104 as an evaporator and the outdoor heat exchanger 105 as a condenser during cooling operation. On the other hand, the air conditioner 101 uses the indoor heat exchanger 104 as a condenser and the outdoor heat exchanger 105 as an evaporator during heating operation.

  In FIG. 1, a solid line arrow X indicates the circulation direction of the gaseous refrigerant (working fluid) during the cooling operation, and a broken line arrow Y indicates the refrigerant circulation direction during the heating operation. The air conditioner 101 operates as follows, for example, during cooling operation.

During the cooling operation, first, the air conditioner 101 compresses the refrigerant with the scroll compressor S. At this time, the refrigerant is compressed to be in a high temperature and high pressure state. The air conditioner 101 sends the refrigerant in that state to the outdoor heat exchanger 105 via the four-way valve 102.
In the outdoor heat exchanger 105, the refrigerant exchanges heat with the air, dissipates heat by the heat exchange, and condenses. The air conditioner 101 sends the condensed refrigerant into the cooling / heating throttle device 103.
In the cooling / heating throttle device 103, the refrigerant is expanded by equal enthalpy and is in a gas-liquid two-phase flow state in which a low-temperature and low-pressure gas refrigerant and a liquid refrigerant are mixed. The air conditioner 101 sends the refrigerant in that state to the indoor heat exchanger 104.
In the indoor heat exchanger 104, the liquid refrigerant exchanges heat with air, absorbs heat and vaporizes by the heat exchange, and becomes a gas refrigerant. At this time, the indoor heat exchanger 104 cools the surrounding air by vaporizing the liquid refrigerant. As a result, the air conditioner 101 exhibits a cooling function.
Thereafter, the air conditioner 101 returns the refrigerant from the indoor heat exchanger 104 to the scroll compressor S. The air conditioner 101 again compresses the refrigerant with the scroll compressor S, and then sequentially sends the refrigerant to the four-way valve 102, the outdoor heat exchanger 105, the cooling / heating throttle device 103, and the indoor heat exchanger 104.
Thus, in the air conditioner 101, the scroll compressor S, the four-way valve 102, the outdoor heat exchanger 105, the cooling / heating throttle device 103, and the indoor heat exchanger 104 constitute a refrigerant circulation system, and the refrigerant is between them. The refrigeration cycle is formed by repeating the circulation.

<Configuration of scroll compressor>
(Overall configuration of scroll compressor)
Hereinafter, the configuration of the scroll compressor S will be described with reference to FIG. FIG. 2 is a cross-sectional view of the scroll compressor S. In the first embodiment, description will be made assuming that the scroll compressor S is a vertical device. The scroll compressor S uses, for example, R32 refrigerant or the like as a working fluid.

  As shown in FIG. 2, the scroll compressor S includes a hermetic container 1 called “chamber”, an electric motor 2 disposed inside the hermetic container 1, an inner part of the hermetic container 1, and an electric motor. 2, and a crankshaft 6 that transmits the rotational power of the electric motor 2 to the scroll compression mechanism 3. The scroll compressor S is characterized by an oil supply mechanism that supplies lubricating oil from the space on the compression chamber 51 side to the space on the suction chamber 4 side. The structure of the lubrication mechanism is described in the chapters “Lubrication mechanism from the compression chamber side space to the suction chamber side space” and “Lubrication operation from the compression chamber side space to the suction chamber side space”. explain in detail.

  The sealed container 1 includes a cylindrical tube chamber 1a, a lid chamber 1b welded to the upper portion of the tube chamber 1a, and a bottom chamber 1c welded to the lower portion of the tube chamber 1a. A sealed chamber space 54 is formed inside the sealed container 1. When the scroll compressor S is operated, a relatively high discharge pressure Pd (not shown) is applied into the chamber inner space 54. Hereinafter, the chamber inner space 54 may be referred to as “discharge pressure space”.

  A suction pipe 7 is fixedly disposed on the side surface or the upper surface of the lid chamber 1b by welding or brazing. The suction pipe 7 is attached to a suction chamber 4 (see FIG. 3) provided in the scroll compression mechanism 3.

  FIG. 3 is a cross-sectional view of the fixed scroll 12 and the orbiting scroll 11 of the scroll compression mechanism 3. 3 shows a configuration in which the fixed scroll 12 and the orbiting scroll 11 are combined, and the orbiting scroll 11 is cut along the upper surface of the orbiting end plate 11b (see FIG. 4) of the orbiting scroll 11 and the configuration is viewed from below. Shows the state. Note that FIG. 3 shows an oil pump 11d described later for convenience of explanation. However, since the oil pump 11d is a component formed on the turning end plate 11b, it is a component that is not originally included in the configuration shown in FIG.

Further, a discharge pipe 8 is fixedly disposed on the side surface of the cylinder chamber 1a by welding or brazing. The discharge pipe 8 is attached to a discharge port 5 (see FIGS. 2 and 3) provided in the scroll compression mechanism 3.
The discharge port 5 communicates with the chamber inner space (discharge pressure space) 54, and communicates the chamber inner space 54 with the outside of the scroll compressor S via the discharge pipe 8. The scroll compressor S is a so-called high pressure chamber type compressor in which the chamber inner space 54 is in a high pressure atmosphere.

  Inside the hermetic container 1, oil (lubricating oil) is sealed at an appropriate stage when the scroll compressor S is assembled. As a result, an oil reservoir 9 is formed at the bottom of the sealed container 1.

  The electric motor 2 includes a stator 2a and a rotor 2b. The stator 2a is fixed to the sealed container 1 by shrink fitting, welding, or the like. The rotor 2b is rotatably arranged inside the stator 2a. A crankshaft 6 is fixed to the rotor 2b.

  The crankshaft 6 includes a main shaft and a pin portion 6c that is an eccentric portion. The main shaft of the crankshaft 6 is supported on a main bearing 13a provided on a frame 13 described later on the upper side, and supported on a lower bearing 10 on the lower side. When the electric motor 2 is driven to rotate the crankshaft 6, the pin portion 6c performs an eccentric rotational movement with respect to the main shaft. The crankshaft 6 is provided with a main bearing 13a, a lower bearing 10, and an oil supply vertical hole 6a and an oil supply horizontal hole 6b for supplying the oil in the oil storage part 9 to a swing bearing part 11c described later.

  The scroll compression mechanism 3 (see FIG. 2) includes a revolving scroll 11, a fixed scroll 12, a frame 13, an Oldham ring 14, a release valve device 15, and a back pressure control valve that is a component of the back pressure control mechanism 40. 45.

  The orbiting scroll 11 has an orbiting scroll wrap 11a, an orbiting end plate 11b, and an orbiting bearing portion 11c. The orbiting scroll wrap 11a is a spiral wrap formed to stand on the orbiting end plate 11b. The slewing bearing portion 11 c is a bearing portion into which a pin portion 6 c that is an eccentric portion of the crankshaft 6 is inserted.

  The fixed scroll 12 has a fixed scroll wrap 12a and a fixed end plate 12b. The fixed scroll wrap 12a is a spiral wrap formed so as to stand on the fixed end plate 12b. A suction chamber 4 is disposed on the outer peripheral portion of the fixed scroll wrap 12a. A discharge port 5 is disposed at the center of the fixed scroll wrap 12a. The suction chamber 4 is a space before the compression chamber 51 is formed, and is divided into a space on the compression chamber 51 side and a space on the suction chamber 4 side when the compression chamber 51 is formed. When the scroll compressor S is operated, a suction pressure Ps (not shown) lower than the discharge pressure Pd (not shown) is applied to the suction chamber 4.

  The orbiting scroll 11 is disposed to face the fixed scroll 12 so as to be orbitable. The scroll compression mechanism 3 communicates with the suction chamber 4 between the fixed scroll wrap 12a and the orbiting scroll wrap 11a by rotating the orbiting scroll 11 with the fixed scroll wrap 12a and the orbiting scroll wrap 11a engaged with each other. A compression chamber 51 is formed (see FIG. 3). Two compression chambers 51 are formed on the outer line side and the inner line side of the orbiting scroll wrap 11a. Hereinafter, the compression chamber 51 formed on the outer line side of the orbiting scroll wrap 11a is referred to as “outer line side compression chamber 51a (see FIG. 3)”, and the compression chamber 51 formed on the inner line side of the orbiting scroll wrap 11a is referred to as “inner line side”. This is referred to as a compression chamber 51b (see FIG. 3).

  Returning to FIG. 2, the outer peripheral side of the frame 13 is fixed to the inner wall surface of the sealed container 1 by welding. The frame 13 includes a main bearing 13 a that rotatably supports the main shaft of the crankshaft 6. The fixed scroll 12 is fastened and fixed to the frame 13 by bolts. A back pressure chamber 53 is formed between the orbiting scroll 11 and the frame 13. The back pressure chamber 53 applies a back pressure Pb (not shown) in a direction from the turning scroll 11 side to the fixed scroll 12 side to the refrigerant. As a result, the scroll compression mechanism 3 presses the orbiting scroll 11 toward the fixed scroll 12 with the refrigerant applied with the back pressure Pb (not shown) so that the orbiting scroll 11 does not move away from the fixed scroll 12. The back pressure Pb (not shown) is set to a substantially intermediate pressure between the discharge pressure Pd (not shown) and the suction pressure Ps (not shown).

  The Oldham ring 14 is disposed between the orbiting scroll 11 and the frame 13. The Oldham ring 14 is a rotation restricting member for causing the fixed scroll 12 to perform a turning motion without rotating the turning scroll 11. The Oldham ring 14 includes a key portion (not shown). The key portion is inserted into a turning Oldham groove (not shown) formed in the orbiting scroll 11 and a frame Oldham groove (not shown) formed in the frame 13. As a result, the Oldham ring 14 regulates the rotation of the orbiting scroll 11.

  The release valve device 15 is a device for releasing pressure from the compression chamber 51 to the chamber inner space 54 so that the pressure in the compression chamber 51 does not become too high.

(Configuration of back pressure control mechanism)
A back pressure control mechanism 40 is provided around the back pressure chamber 53. Hereinafter, the configuration of the back pressure control mechanism 40 will be described with reference to FIG. FIG. 4 is a partially enlarged cross-sectional view of the back pressure control mechanism 40 and its surroundings.

  As shown in FIG. 4, the back pressure control mechanism 40 includes a back pressure valve communication passage 41 that communicates the compression chamber 51 and the back pressure chamber 53, and a back pressure control valve that is disposed in the middle of the extension of the back pressure valve communication passage 41. 45.

  The back pressure valve communication passage 41 has an outer circumferential relief groove 12 d, a bay-shaped recess 12 e, a back pressure valve inflow hole 42, and a back pressure chamber oil outflow passage 44.

  The back pressure valve inflow hole 42 is a vertical hole formed so as to extend upward from the fixed end plate 12 c of the fixed scroll 12. The back pressure valve inflow hole 42 functions as back pressure chamber oil inflow means for allowing the refrigerant mixed with oil to flow into the back pressure chamber 53. The back pressure valve inflow hole 42 has a lower opening 42 a communicating with the bay-shaped recess 12 e and an upper side communicating with the back pressure valve hole 43. Here, the opening 42a of the back pressure valve inflow hole 42 has a revolving end plate 11b of the revolving scroll 11 that revolves when the revolving scroll 11 is revolved with the fixed scroll wrap 12a and the revolving scroll wrap 11a engaged. Always covered. As a result, the opening 42 a of the back pressure valve inflow hole 42 does not directly open into the back pressure chamber 53. The back pressure valve inflow hole 42 and the back pressure chamber 53 communicate with each other through an outer peripheral relief groove 12 d and a bay-shaped recess 12 e formed in the fixed end plate 12 c of the fixed scroll 12.

  The back pressure chamber oil outflow passage 44 is formed between the back pressure chamber 53 and the compression chamber 51 and is a flow path for supplying oil in the back pressure chamber 53 to the compression chamber 51. The opening 44 a that faces the compression chamber 51 of the back pressure chamber oil outflow path 44 functions as an oil introduction portion that introduces oil into the compression chamber 51. Hereinafter, the opening 44a of the back pressure chamber oil outflow passage 44 may be referred to as an “oil introduction portion 44a”. In the example shown in FIG. 3, four oil introducing portions 44 a are formed on the fixed end plate 12 c of the fixed scroll 12. Therefore, the scroll compressor S is configured to introduce oil into the compression chamber 51 from the four oil introduction portions 44a.

  The back pressure control valve 45 has a valve body 45a and a coiled spring 45b. The valve body 45a is formed of a plate body, and is disposed so as to close the upper end opening of the back pressure valve inflow hole 42, that is, the opening opposite to the opening 42a.

  The coiled spring 45 b is a spring spring and is disposed between the valve body 45 a and the press-fitting member 20. One end side of the coiled spring 45 b is supported by the press-fitting member 20, thereby urging the valve body 45 a disposed on the other end side toward the upper end opening of the back pressure valve inflow hole 42.

  Such a back pressure control valve 45 is configured such that when the pressure in the back pressure chamber 53 rises above a predetermined pressure difference from the pressure in the compression chamber 51, the valve body 45a becomes the urging force of the coiled spring 45b. The valve is opened by lifting it against it. The back pressure control valve 45 controls the pressure in the back pressure chamber 53 (back pressure Pb (not shown)) by communicating the back pressure chamber 53 and the compression chamber 51 by this valve opening operation.

  Such a back pressure control valve 45 is attached to the fixed scroll 12 through a back pressure valve hole 43. The back pressure valve hole 43 is formed in the fixed scroll 12 so as to face the extension of the back pressure valve communication passage 41. The back pressure valve hole 43 is closed by the press-fitting member 20 being press-fitted through the opening after the back pressure control valve 45 is disposed at a predetermined position.

(Structure of the oil supply mechanism from the space on the compression chamber side to the space on the suction chamber side)
The scroll compressor S includes an oil supply mechanism from the space on the compression chamber 51 side to the space on the suction chamber 4 side. Hereinafter, the configuration of the oil supply mechanism will be described with reference to FIGS. 3, 5, and 6. This oil supply mechanism is characterized by having an oil drawing portion 11d. FIG. 5 is a configuration diagram of the orbiting scroll 11 as viewed from below. FIG. 6 is a cross-sectional view of the orbiting scroll 11 viewed from the side.

  As shown in FIGS. 3, 5, and 6, the orbiting end plate 11 b of the orbiting scroll 11 is formed with an oil scooping portion 11 d that draws oil inside the compression chamber 51 and supplies it to the suction chamber 4. Yes.

  The oil drawing portion 11d is formed as a recess, hole, or groove. In the first embodiment, description will be made assuming that the oil scooping portion 11d is a conical depression. The oil scooping portion 11 d is provided closer to the suction chamber 4 than the end of winding of the orbiting scroll 11 (the end on the discharge port 5 side). The oil scooping part 11d moves with the orbiting motion of the orbiting scroll 11, and communicates alternately with the inside of the space on the compression chamber 51 side partitioned by the fixed scroll wrap 12a and the inside of the space on the suction chamber 4 side. To do. At that time, the oil pumping part 11d pumps oil in the space on the compression chamber 51 side, brings the pumped oil into the space on the suction chamber 4 side, and supplies it to the space on the suction chamber 4 side.

  Here, the operation “alternatingly communicates with the inside of the space on the compression chamber 51 side and the inside of the space on the suction chamber 4 side” means that the oil drawing section 11 d is located on the inside of the space on the compression chamber 51 side and the side of the suction chamber 4. This means an operation that communicates with only one of the interiors of the space and does not communicate with both at the same time.

  In the first embodiment, the oil scooping part 11 d moves so as to turn under the tip of the fixed scroll wrap 12 a as the turning scroll 11 turns. As a result, the oil scooping portion 11d communicates with the space on the compression chamber 51 side on the outer peripheral side of the space, and communicates with the space on the suction chamber 4 side on the inner peripheral side of the space. The size of the oil scooping portion 11d is such that the space on the compression chamber 51 side and the space on the suction chamber 4 side do not communicate with each other via the oil scooping portion 11d so that the fixed scroll wrap 12a is within the moving range of the oil scooping portion 11d. The value is set smaller than the thickness. In addition, the oil scooping part 11d moves along a movement locus Lo11d shown in FIG. 7A, for example. The above-mentioned “movement range of the oil drawing part 11d” means a range when the oil drawing part 11d moves along the movement locus Lo11d.

  The communication area between the space on the suction chamber 4 side and the oil drawing part 11d is set to a value larger than the communication area between the space on the compression chamber 51 side and the oil drawing part 11d. Thus, the scroll compressor S can efficiently supply the oil pumped from the space on the compression chamber 51 side by the oil pumping portion 11d to the space on the suction chamber 4 side. That is, as a result, the scroll compressor S is not supplied to the space on the suction chamber 4 side without being pumped up by the oil pumping portion 11d, and remains in the space on the compression chamber 51 side. Returning can be suppressed.

<Operation of scroll compressor>
Hereinafter, regarding the main operation of the scroll compressor S, the refrigerant compression operation will be described first, and then the oil supply operation will be described.

(Refrigerant compression operation)
First, the refrigerant compression operation of the scroll compressor S will be described mainly with reference to FIG.
In the scroll compressor S, when the electric motor 2 is driven and the crankshaft 6 rotates, the pin portion 6c of the crankshaft 6 rotates eccentrically. At this time, since the Oldham ring 14 restricts the rotation of the orbiting scroll 11, the orbiting scroll 11 performs an orbiting motion with the eccentric rotation of the pin portion 6c. By this series of operations, the refrigerant sucked into the scroll compressor S from the suction pipe 7 is sent to the compression chamber 51 through the suction chamber 4 and is compressed in the compression chamber 51.

Thereafter, the refrigerant is discharged from the discharge port 5 into the chamber internal space 54 that is a discharge pressure space. Then, the refrigerant is discharged from the discharge pipe 8 to the outside of the scroll compressor S. The refrigerant discharged to the outside circulates in the refrigeration cycle of the air conditioner 101 (see FIG. 1) and is returned from the suction pipe 7 to the inside of the scroll compressor S.
The scroll compressor S repeats such an operation.

(Oil supply operation from oil storage part to compression chamber)
Next, with reference mainly to FIG.2 and FIG.3, it demonstrates per oil supply operation | movement from the oil storage part 9 of the scroll compressor S to the compression chamber 51. FIG.

  In the scroll compressor S, the pressure in the back pressure chamber 53 is changed by the back pressure control valve 45 from the back pressure Pb which is a substantially intermediate pressure between the discharge pressure Pd (not shown) and the suction pressure Ps (not shown). (Not shown). Therefore, a differential pressure is generated between the oil storage unit 9 and the back pressure chamber 53. With this differential pressure, the oil in the oil storage section 9 passes from the oil supply piece fixedly arranged at the lower end of the crankshaft 6 through the oil supply vertical hole 6a, through the oil supply horizontal hole 6b and the slit portion (not shown) provided in the crankshaft 6. Then, the lubricant flows into the back pressure chamber 53 while lubricating the swing bearing portion 11c and the main bearing 13a.

  The oil flowing into the back pressure chamber 53 flows into the compression chamber 51 through a back pressure valve communication passage 41 provided with a back pressure control valve 45 in the middle due to the differential pressure between the back pressure chamber 53 and the compression chamber 51. To do. The oil that has flowed into the compression chamber 51 is discharged into the chamber inner space 54 from the discharge port 5 together with the refrigerant while improving the sealing performance of the compression chamber 51. The oil discharged from the discharge port 5 is separated from the refrigerant in the chamber inner space 54 and returns to the oil storage section 9 formed in the lower portion of the chamber inner space 54.

(Lubrication operation from the space on the compression chamber side to the space on the suction chamber side)
Next, mainly with reference to FIG. 7, an oil supply operation from the compression chamber 51 of the scroll compressor S to the suction chamber 4 will be described. FIG. 7 is an explanatory diagram of the operation of the scroll compressor S. The orbiting scroll 11 orbits as the crankshaft 6 rotates. FIG. 7 shows a series of movements of the compression chamber 51, the oil scooping portion 11d, and the like accompanying the turning motion of the turning scroll 11.

  FIG. 7A to FIG. 7F show states of the orbiting scroll 11 when the crank angles are 0 °, 90 °, 120 °, 160 °, 230 °, and 245 °, respectively. Fig.7 (a) has shown the state when the outer side compression chamber 51a of the turning scroll wrap 11a begins to form. Here, description will be made assuming that the crank angle in the state shown in FIG. 7A is 0 °. However, the values of the crank angles of 0 °, 90 °, 120 °, 160 °, 230 °, and 245 ° described above are merely examples, and vary depending on the design of the scroll compressor S.

  In the example shown in FIG. 7, only the one closest to the back pressure valve inflow hole 42 (see FIG. 3) is shown among the four oil introduction portions 44a shown in FIG. 3, and the others are omitted. Yes.

  In the example shown in FIG. 7A, a refrigerant flow path for supplying a refrigerant to the compression chamber 51 is formed between the suction chamber 4 and the compression chamber 51, and the suction in the refrigerant flow path A space A1 from the chamber 4 to the oil introduction portion 44a is a space in which oil tends to be insufficient. The present invention intends to sufficiently supply an amount of oil necessary for sealing the front ends and the side surfaces of the scroll wraps 11a and 12a in the space A1 where oil tends to be insufficient. Therefore, in the first embodiment, as shown in FIG. 5, the oil scooping portion 11d is disposed in the vicinity of the upstream end P11a of the orbiting scroll wrap 11a and slightly upstream from the upstream end P11a. . As shown in FIG. 7 (a), this position is such that when the oil pumping part 11d moves along the movement locus Lo11d (see FIG. 7 (a)), the oil pumping part with respect to the space on the suction chamber 4 side. This is a position where 11d can enter the position in the vicinity of the suction chamber 4 and slightly downstream of the suction chamber 4. The scroll compressor S supplies the oil to a position slightly downstream of the suction chamber 4 by disposing the oil scooping portion 11d at this position, so that each scroll wrap 11a in the space A1 where oil tends to be insufficient. , 12a can be sufficiently supplied with an amount of oil necessary for sealing the tip and side surfaces.

  The refueling operation from the compression chamber 51 to the suction chamber 4 is started from, for example, the state shown in FIG. 7B (the state where the crank angle is 90 °). FIG. 7B shows a state of the orbiting scroll 11 after the oil scooping part 11d supplies oil to the space on the suction chamber 4 side. In the state shown in FIG. 7B, the oil scooping portion 11d is disposed under the fixed scroll wrap 12a and is not in communication with the space on the suction chamber 4 side or the space on the compression chamber 51 side. It has become.

  When the rotation of the crankshaft 6 proceeds after FIG. 7B, the orbiting scroll 11 is sequentially in the state shown in FIG. 7C (the crank angle is 120 °, as will be described below). ), A state shown in FIG. 7D (a state where the crank angle is 160 °), and a state shown in FIG. 7E (a state where the crank angle is 230 °).

  First, in the state shown in FIG. 7C, the oil scooping part 11d moves from below the fixed scroll wrap 12a to the compression chamber 51 side. Thereby, the oil scooping part 11d starts to communicate with the space on the compression chamber 51 side.

  Next, in the state shown in FIG. 7D, the oil scooping portion 11d further moves to the compression chamber 51 side. Accordingly, the oil scooping portion 11d is disposed at a position that intersects the wrap wall surface on the tip side of the fixed scroll wrap 12a (the end plate side of the orbiting scroll wrap 11a) below the fixed scroll wrap 12a. At this time, the oil pumping unit 11d pumps oil from the space on the compression chamber 51 side. The oil pressure at this time is (suction pressure + α). Here, “α” represents the pressure for compressing the oil.

  Next, in the state shown in FIG. 7E, the oil scooping portion 11d moves from the space on the compression chamber 51 side to the suction chamber 4 side. Thereby, the oil scooping part 11d is arranged under the fixed scroll wrap 12a. At this time, the oil scooping part 11d is in a state of not communicating with the space on the compression chamber 51 side and the space on the suction chamber 4 side.

  When the rotation of the crankshaft 6 proceeds after FIG. 7 (e), the orbiting scroll 11 is sequentially in the state shown in FIG. 7 (f) (the crank angle is 245 °) as described below. ), The state shown in FIG. 7A (the crank angle is 0 °), and the state shown in FIG. 7B (the crank angle is 90 °).

  First, in the state shown in FIG. 7F, the oil scooping portion 11d moves from the bottom of the fixed scroll wrap 12a to the suction chamber 4 side. Thereby, the oil scooping part 11d starts to communicate with the space on the suction chamber 4 side.

  Next, in the state shown in FIG. 7A, the oil scooping portion 11d further moves to the suction chamber 4 side. Thereby, the whole oil-drawing part 11d is arrange | positioned in the space by the side of the suction chamber 4. FIG. At this time, the oil pumping part 11d supplies the oil pumped in the space on the compression chamber 51 side to the space on the suction chamber 4 side. The oil pressure at this time is (suction pressure + α).

Next, in the state shown in FIG. 7B, the oil scooping portion 11d moves from the space on the suction chamber 4 side to the compression chamber 51 side. Thereby, the oil scooping part 11d is arranged under the fixed scroll wrap 12a. At this time, the oil scooping part 11d is in a state of not communicating with the space on the compression chamber 51 side and the space on the suction chamber 4 side.
The scroll compressor S repeats such an operation.

  In such a configuration, in the scroll compressor S, with the turning motion of the orbiting scroll 11, the oil scooping portion 11 d communicates alternately with the inside of the space on the compression chamber 51 side and the inside of the space on the suction chamber 4 side. Thereby, the scroll compressor S can form an intermittent oil supply path from the space on the compression chamber 51 side to the space on the suction chamber 4 side.

  Such a scroll compressor S seals the front ends and side surfaces of the respective scroll wraps 11a and 12a against the space A1 in which the oil from the suction chamber 4 to the oil introduction portion 44a in the refrigerant channel tends to be insufficient. Therefore, it is possible to sufficiently supply the necessary amount of oil. Therefore, the scroll compressor S can improve the seals of the tip and side surfaces of the respective scroll wraps 11a and 12a in the compression chamber 51, and can suppress the leakage of the refrigerant.

  Further, the scroll compressor S does not supply the lubricating oil in the back pressure chamber 53 (that is, the oil on which the back pressure Pb is applied) to the space on the suction chamber 4 side, unlike the conventional scroll compressor, Oil in the space on the compression chamber 51 side (that is, oil that is lower than the back pressure Pb (suction pressure Ps + α)) is supplied to the space on the suction chamber 4 side. Such a scroll compressor S can supply oil in a lower temperature and low pressure state than the oil in the back pressure chamber 53 to the space on the suction chamber 4 side.

  Therefore, the scroll compressor S does not bring the refrigerant into contact with the lubricating oil in the high-temperature and high-pressure state in the suction chamber 4 unlike the conventional scroll compressor, so the heat loss in the suction chamber 4 (volume efficiency of the refrigerant) ) And re-expansion loss (decrease in the amount of refrigerant supplied to the suction chamber) can be reduced.

  Further, as a further effect, the scroll compressor S compresses the oil supplied to the suction chamber 4 because the oil once supplied to the suction chamber 4 passes through the compression chamber 51 and returns to the suction chamber 4 at the oil pumping portion 11d. Circulation can be repeated between the space on the chamber 51 side and the space on the suction chamber 4 side. As a result, for example, the scroll compressor S secures a certain amount of oil in the space A1 (see FIG. 7A) in which the oil from the suction chamber 4 to the oil introduction portion 44a in the refrigerant channel tends to be insufficient. Therefore, the refrigerant leakage loss can be reliably reduced.

  Further, in the scroll compressor S, the formation position and size of the oil scooping portion 11d are set to a position (a position that does not enter) and a size that only partially communicates with the interior of the space on the compression chamber 51 side. That is, even when the groove opening area is the maximum in the section where the oil pumping section 11d pumps the oil from the compression chamber 51 (the section where the crank angle is 120 ° to 230 ° in the first embodiment), the groove The oil pumping portion 11d is formed at a position where the oil is not fully opened. The inside of the compression chamber 51 is in a mixed state of oil and refrigerant. However, the scroll compressor S is configured so that the oil pumping unit 11d has a higher oil ratio in the course of the oil supply operation from the space on the compression chamber 51 side to the space on the suction chamber 4 side by the oil pumping unit 11d. The oil supply efficiency can be improved. In the first embodiment, the scroll compressor S moves the oil scooping portion 11d below the fixed scroll wrap 12a at the bottom of the fixed scroll wrap 12a when pumping the oil shown in FIGS. 7 (d) and 7 (e). Is disposed at a position intersecting with the wrap wall surface on the tip end side (the end plate side of the orbiting scroll wrap 11a). That is, the scroll compressor S opens the oil pumping portion 11d in a region where the oil on the wrap wall surface is adhered (region with a high oil ratio) when pumping oil. Thereby, the scroll compressor S can improve the oil supply efficiency.

  In such a configuration, in the compression chamber 51 of the scroll compressor S according to the first embodiment, the refrigerant increases as it proceeds from the upstream side (the side far from the discharge port 5) to the downstream side (the side closer to the discharge port 5). Compressed to density. Therefore, the refrigerant becomes hot and high pressure as it goes downstream. Therefore, the refrigerant is in a low temperature and low pressure state on the upstream side than on the downstream side. The scroll compressor S draws lubricating oil on the upstream side and supplies the lubricating oil to the suction chamber 4 so that the lubricating oil in a lower temperature and low pressure state than the downstream side (side closer to the discharge port 5) is supplied to the suction chamber 4. Supply. Even if the lubricating oil comes into contact with the refrigerant in the suction chamber 4, it does not cause heating loss (decrease in volumetric efficiency of the refrigerant) or reexpansion loss (decrease in the amount of refrigerant supplied to the suction chamber). Low temperature and low pressure. Therefore, the scroll compressor S can reduce the rise in the temperature of the refrigerant in the suction chamber 4 more than the conventional scroll compressor, and as a result, the heat loss in the suction chamber 4 (decrease in the volumetric efficiency of the refrigerant). ) Can be reduced. Further, the scroll compressor S can suppress the expansion of the lubricating oil and the refrigerant in the suction chamber 4 more than the conventional scroll compressor, and as a result, the increase in the pressure in the suction chamber 4 is suppressed. The re-expansion loss in the suction chamber 4 (decrease in the amount of refrigerant supplied to the suction chamber) can be reduced.

  In addition, when the scroll compressor S sends out the oil supplied to the back pressure chamber 53 from the back pressure chamber 53 to the compression chamber 51, the space shown by hatching in FIG. Oil can be dissipated in the back pressure communication passage 41) from the provided space to the compression chamber 51. Thereby, the scroll compressor S can reduce the temperature of oil a little. Further, the scroll compressor S can divide the back pressure chamber 53 by the back pressure control valve 45 from the hatched space in FIG. It is possible to slightly reduce the pressure applied to the oil inside the space indicated by slanting lines rather than the existing pressure. The scroll compressor S can further reduce heating loss and re-expansion loss more efficiently by supplying the suction chamber 4 with oil whose temperature and pressure have been reduced.

  Further, the scroll compressor S has, for example, tips of the scroll wraps 11a and 12a in a space A1 (see FIG. 7A) in which the oil from the suction chamber 4 to the oil introduction portion 44a in the refrigerant flow path tends to be insufficient. The amount of oil necessary for sealing the part and the side can be sufficiently supplied.

  As described above, according to the scroll compressor S according to the first embodiment, for example, the space A1 in which the oil from the suction chamber 4 in the refrigerant flow path to the oil introduction portion 44a tends to be insufficient (FIG. 7A). In reference), it is possible to reduce heating loss and re-expansion loss in the suction chamber 4 while sufficiently supplying an amount of oil necessary for sealing the tip and side surfaces of the scroll wraps 11a and 12a. . Thereby, the air conditioner 101 provided with the scroll compressor S can improve a coefficient of performance (COP).

[Second Embodiment]
Hereinafter, the configuration of the scroll compressor SA according to the second embodiment will be described with reference to FIG. FIG. 8 is a cross-sectional view of the fixed scroll 12 and the orbiting scroll 11 of the scroll compressor SA according to the second embodiment as viewed from below.

  As shown in FIG. 8, the scroll compressor SA according to the second embodiment has an arcuate groove that is connected to the suction chamber 4 on the fixed end plate 12 c of the fixed scroll 12 as compared with the scroll compressor S according to the first embodiment. 12 f is provided, the position of the oil pumping part 11 d is moved to the vicinity of the back pressure chamber oil outflow path 44, and the oil in the space on the compression chamber 51 side is supplied to the arc-shaped groove 12 f by the oil pumping part 11 d. Yes. In such a configuration, the oil scooping portion 11d is formed on the arc-shaped groove 12f side from the oil introducing portion 44a, and moves with the orbiting motion of the orbiting scroll 11, so that the inside of the space on the compression chamber 51 side and the arc-shaped shape are moved. It communicates alternately with the inside of the groove 12f.

  Such a scroll compressor SA can transport oil by the oil scooping part 11d in a place close to the back pressure chamber oil outflow passage 44, and therefore more reliably supply oil to the space on the suction chamber 4 side. Can do.

Further, since the scroll compressor SA draws oil on the upstream side of the compression chamber 51 with respect to the scroll compressor S of the first embodiment, the oil in the low temperature and low pressure state is sucked into the suction chamber than the scroll compressor S of the first embodiment. It can be supplied to the four-side space.
Furthermore, the scroll compressor SA supplies the lubricating oil from the space on the compression chamber 51 side to the space on the suction chamber 4 side at a location outside the refrigerant flow path. Therefore, the scroll compressor SA can supply the lubricating oil to the space on the suction chamber 4 side without disturbing the flow of the refrigerant.
Due to these factors, the scroll compressor SA can reduce the heating loss and the re-expansion loss in the suction chamber 4 more efficiently than the scroll compressor S of the first embodiment. As a result, the scroll compressor SA can improve the coefficient of performance (COP) of the air conditioner than the scroll compressor S of the first embodiment.

As described above, according to the scroll compressor SA according to the second embodiment, similarly to the scroll compressor S according to the first embodiment, the leading ends of the scroll wraps 11a and 12a in a space where oil tends to be insufficient. It is possible to reduce heating loss and re-expansion loss in the suction chamber 4 while sufficiently supplying an amount of oil necessary for sealing the portion and the side surface. Thereby, the air conditioner 101 provided with scroll compressor SA can improve a coefficient of performance (COP).
Moreover, according to the scroll compressor SA, the heating loss and the re-expansion loss in the suction chamber 4 can be reduced more efficiently than the scroll compressor S according to the first embodiment.

[Third Embodiment]
Hereinafter, the configuration of the scroll compressor SB according to the third embodiment will be described with reference to FIG. FIG. 9 is a cross-sectional view of the fixed scroll 12 and the orbiting scroll 11 of the scroll compressor SB according to the third embodiment as viewed from below.

  As shown in FIG. 9, the scroll compressor SB according to the third embodiment is different from the scroll compressor SA according to the second embodiment in that the oil scooping portion 11d is added to two. ing.

  Such a scroll compressor SB can increase the amount of oil supplied from the space on the compression chamber 51 side to the space on the suction chamber 4 side than the scroll compressor SA according to the second embodiment. The sealing performance in the space A1, which tends to be insufficient, can be further improved, and the reduction of refrigerant leakage can be improved.

As described above, according to the scroll compressor SB according to the third embodiment, similarly to the scroll compressors S and SA according to the other embodiments, the scroll wraps 11a and 12a in a space where oil tends to be insufficient. It is possible to reduce heating loss and re-expansion loss in the suction chamber 4 while supplying a sufficient amount of oil necessary for sealing the tip and side surfaces of the suction chamber 4. Thereby, the air conditioner 101 provided with the scroll compressor SB can improve a coefficient of performance (COP).
Moreover, according to the scroll compressor SB, similarly to the scroll compressor SA according to the second embodiment, the heating loss and re-expansion loss in the suction chamber 4 can be performed more efficiently than the scroll compressor S according to the first embodiment. Can be reduced.
In addition, according to the scroll compressor SB, it is possible to further improve the sealing performance in the space A1 where oil tends to be insufficient compared to the scroll compressor SA according to the second embodiment, and to reduce the leakage of refrigerant. Can be improved.

[Fourth Embodiment]
Hereinafter, the configuration of the scroll compressor SC according to the fourth embodiment will be described with reference to FIG. FIG. 10 is a cross-sectional view of the fixed scroll 12 and the orbiting scroll 11 of the scroll compressor SC according to the fourth embodiment as viewed from below.

  As shown in FIG. 10, the scroll compressor SC according to the fourth embodiment is different from the scroll compressor SA according to the second embodiment in that the oil scooping portion 11d is formed in a long hole shape. doing.

  Such a scroll compressor SC can further increase the oil pumping capacity of the oil pumping unit 11d as compared with the scroll compressor SA according to the second embodiment and the scroll compressor SB according to the third embodiment. As a result, the scroll compressor SC can further increase the amount of oil supplied from the space on the compression chamber 51 side to the space on the suction chamber 4 side. Therefore, the scroll compressor SC can further improve the sealing performance in the space A1 where the oil tends to be insufficient compared to the scroll compressor SA according to the second embodiment and the scroll compressor SB according to the third embodiment. Further, it is possible to improve the reduction of refrigerant leakage.

As described above, according to the scroll compressor SC according to the fourth embodiment, similarly to the scroll compressors S, SA, SB according to the other embodiments, each scroll wrap 11a in a space where oil tends to be insufficient. , 12a, the heating loss and the re-expansion loss in the suction chamber 4 can be reduced while sufficiently supplying an amount of oil necessary for sealing the tip and side surfaces. Thereby, the air conditioner 101 provided with the scroll compressor SC can improve a coefficient of performance (COP).
Moreover, according to the scroll compressor SC, similarly to the scroll compressors SA and SB according to the second and third embodiments, the heat loss in the suction chamber 4 is more efficient than the scroll compressor S according to the first embodiment. And reexpansion loss can be reduced.
In addition, according to the scroll compressor SC, it is possible to further improve the sealing performance in the space A1 where oil tends to be insufficient compared to the scroll compressor SB according to the third embodiment, and to reduce the leakage of refrigerant. Can be improved.

  The present invention is not limited to the above-described embodiment, and includes various modifications. For example, the above-described embodiment has been described in detail for easy understanding of the present invention, and is not necessarily limited to one having all the configurations described. Further, a part of the configuration of an embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of an embodiment. In addition, it is possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

DESCRIPTION OF SYMBOLS 1 Airtight container 1a Cylinder chamber 1b Cover chamber 1c Bottom chamber 2 Electric motor 2a Stator 2b Rotor 3, 3A, 3B, 3C Scroll compression mechanism 4 Suction chamber 5 Discharge port 6 Crankshaft 6a Oil supply vertical hole 6b Oil supply horizontal hole 6c Pin part 7 Suction Pipe 8 Discharge pipe 9 Oil storage part 10 Lower bearing 11 Orbiting scroll 11a Orbiting scroll wrap 11b Orbiting end plate 11c Orbiting bearing part 11d Oil scooping part 12 Fixed scroll 12a Fixed scroll wrap 12b Fixed end plate 12c Fixed end plate 12d Outer clearance groove 12e Bay shape Concave portion 12f Arc-shaped groove 13 Frame 13a Main bearing 14 Oldham ring 15 Release valve device 20 Press-fit member 40 Back pressure control mechanism 41 Back pressure valve communication passage 42 Back pressure valve inflow hole 42a Opening portion 43 Back pressure valve hole (mounting hole)
44 Back pressure chamber oil outflow path 44a Opening of back pressure chamber oil outflow path (oil introduction section)
45 Back pressure control valve 45a Valve body 45b Coil spring 51 Compression chamber 51a Outer line side compression chamber 51b Inner line side compression chamber 53 Back pressure chamber 54 Chamber inner space 101 Air conditioner 102 Four-way valve 103 Heating / cooling throttle device 104 Indoor heat exchanger 105 Outdoor heat exchanger 106 Piping Lo11d Movement trajectory of oil pumping part P11a Upstream end of orbiting scroll wrap S, SA, SB, SC Scroll compressor

Claims (10)

A fixed scroll having an end plate and a spiral wrap standing on the end plate;
An orbiting scroll having an end plate and a spiral wrap standing on the end plate, and forming a compression chamber for compressing refrigerant between the fixed scroll; and
A suction chamber for supplying a refrigerant to the compression chamber,
Oil that communicates alternately with the inside of the space on the compression chamber side and the inside of the space on the suction chamber side, which is partitioned by the wrap of the fixed scroll with the orbiting motion of the orbiting scroll, on the end plate of the orbiting scroll A scroll compressor characterized in that a drawing section is formed. The scroll compressor according to claim 1, wherein
The size of the oil scooping section is such that the space on the compression chamber side and the space on the suction chamber side do not communicate with each other via the oil scooping section so that the fixed scroll wraps within the moving range of the oil scooping section. A scroll compressor characterized by being set to a value smaller than the thickness of the scroll compressor. The scroll compressor according to claim 1 or 2,
The scroll pump is characterized in that the oil scooping part moves so as to turn under the tip of the wrap of the fixed scroll in accordance with the turning movement of the turning scroll. The scroll compressor according to claim 1 or 2,
On the end plate of the fixed scroll, an arc-shaped groove connected to the suction chamber is formed as a space on the suction chamber side,
The oil scooping part is formed on the arc-shaped groove side from the oil introducing part for introducing oil into the compression chamber, and the inside of the space on the compression chamber side with the orbiting motion of the orbiting scroll A scroll compressor characterized by alternately communicating with the inside of an arc-shaped groove. The scroll compressor according to claim 4, wherein
A scroll compressor, wherein an end plate of the orbiting scroll is formed with a plurality of the oil scooping portions. The scroll compressor according to claim 4, wherein
A scroll compressor, wherein the end plate of the orbiting scroll is formed with the oil scooping portion having a long hole shape. The scroll compressor according to any one of claims 1 to 6,
The suction chamber is a space before the compression chamber is formed, and is divided into a space on the compression chamber side and a space on the suction chamber side by forming the compression chamber. Scroll compressor. The scroll compressor according to claim 7, wherein
The oil scooping portion communicates with an outer peripheral side of the space with respect to the space on the compression chamber side, and communicates with an inner peripheral side of the space with respect to the space on the suction chamber side. Compressor. The scroll compressor according to claim 7 or 8,
The scroll compressor characterized in that a communication area between the space on the suction chamber side and the oil drawing section is larger than a communication area between the space on the compression chamber side and the oil drawing section. A scroll compressor;
A heat exchanger,
The scroll compressor is
A fixed scroll having an end plate and a spiral wrap standing on the end plate;
An orbiting scroll having an end plate and a spiral wrap standing on the end plate, and forming a compression chamber for compressing refrigerant between the fixed scroll; and
A suction chamber for supplying a refrigerant to the compression chamber,
Oil that communicates alternately with the inside of the space on the compression chamber side and the inside of the space on the suction chamber side, which is partitioned by the wrap of the fixed scroll with the orbiting motion of the orbiting scroll, on the end plate of the orbiting scroll An air conditioner characterized in that a drawing section is formed.

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