JP2019105195A - Compressor - Google Patents

Abstract

To provide a compressor in which a check valve mechanism for suppressing a backflow of a refrigerant into a suction path is provided, and which has high reliability regarding inflow suppression of a liquid refrigerant into the compressor.SOLUTION: A compressor compresses a refrigerant sucked from a suction port 23a in a compression chamber and discharges it from a discharge port. The compressor includes: a suction path 90 for guiding the refrigerant sucked from the suction port to the compression chamber; and a check valve mechanism 80. The check valve mechanism is provided in the suction path. The check valve mechanism suppresses the refrigerant back-flowing to the outside of the compressor from the inside of the compressor through the suction port while the operation of the compressor is stopped. The check valve mechanism includes a valve seat 84, a valve body 82, an elastic member 88, and a magnetic force generating member 84. The valve body is provided in the suction path so as to move along the suction path, and it is pressed against the valve seat, and closes the suction path. The elastic member energizes the valve body toward the valve seat. The magnetic force generating member suppresses the movement of the valve body pressed against the valve seat by a magnetic force.SELECTED DRAWING: Figure 2

Description

  The present disclosure relates to a compressor, in particular, a compressor in which a check valve mechanism is provided in a refrigerant suction path.

  Conventionally, as disclosed in Patent Document 1 (Japanese Patent Application Laid-Open No. 2010-31677), a compressor that compresses and discharges a refrigerant sucked from an inlet (intake port) of a suction pipe, and the inside of the compressor There is known a compressor provided with a check valve mechanism in a suction path for guiding the refrigerant from the suction port to the compression chamber in order to prevent the refrigerant from flowing back to the outside. In the check valve mechanism of Patent Document 1 (Japanese Patent Laid-Open No. 2010-31677), a valve body for opening and closing an opening on one end side of a suction pipe and a valve body are biased from the back side toward the open end face of the suction pipe. It is equipped with a spring.

  By the way, depending on the design of the refrigerant system into which the compressor is incorporated (for example, the layout of the piping on the upstream side of the suction port, etc.), the liquid refrigerant condensed in the refrigerant system at the time of stopping the compressor (Including the inside of the suction path upstream of the valve body of When the amount of liquid refrigerant accumulated in the suction side pipe increases, the force by the weight of the liquid refrigerant exceeds the biasing force of the spring and the valve body of the check valve is moved, which may cause the liquid refrigerant to flow into the compressor. There is. If the liquid refrigerant flows into the interior of the compressor while the compressor is stopped, the liquid refrigerant may cause the oil in the sliding portion in the compressor to flow, which may cause a lubrication failure when the compressor is restarted.

  Patent Document 1 (Japanese Unexamined Patent Publication No. 2010-31677) does not disclose a technique for alleviating such a problem.

  An object of the present disclosure is a compressor provided with a check valve mechanism that suppresses backflow of a refrigerant in a suction path that guides refrigerant drawn from a suction port to a compression chamber, and the liquid refrigerant into the compressor It is an object of the present invention to provide a highly reliable compressor with respect to inflow suppression.

  The compressor compresses the refrigerant sucked from the suction port in the compression chamber and discharges the refrigerant from the discharge port. The compressor includes an intake path and a check valve mechanism. The suction path leads the refrigerant sucked from the suction port to the compression chamber. The check valve mechanism is provided in the suction path. The check valve mechanism suppresses the backflow of the refrigerant from the inside of the compressor to the outside of the compressor through the suction port when the operation of the compressor is stopped. The check valve mechanism has a valve seat, a valve body, an elastic member, and a magnetic force generation member. The valve body is movably provided along the suction path in the suction path, and pressed against the valve seat to close the suction path. The elastic member biases the valve body toward the valve seat. The magnetic force generation member suppresses the movement of the valve body pressed against the valve seat by the magnetic force.

  In this compressor, the movement of the valve pressed against the valve seat is suppressed by the magnetic force in addition to the elastic force of the elastic member, so that the liquid refrigerant from the outside of the compressor to the inside of the compressor through the suction path It is easy to control the flow. Therefore, in the present compressor, even when the liquid refrigerant is accumulated in the pipe on the suction side when the compressor is stopped, the inflow of the liquid refrigerant into the inside of the compressor can be suppressed, and the reliability is high.

  Preferably, in the compressor, the valve seat doubles as a magnetic force generating member.

  Here, since the valve seat itself is a magnetic force generating member, the movement of the valve body can be relatively strongly suppressed by the magnetic force.

  In another example, preferably, in the compressor, the magnetic force generation member is separate from the valve seat.

  Here, since the valve body does not contact the magnetic force generation member directly, the magnetic force generation member is damaged by an impact when the valve body is pressed against the valve seat or a force generated when the valve body is pulled away from the valve seat. Can be prevented.

  In addition, preferably, the compressor further includes a first member that constitutes a part of a compression mechanism that forms the compression chamber. The suction path has a connecting pipe. The communication tube portion is provided closer to the suction port than the valve seat, and is inserted into and fixed to a hole formed in the first member. A groove to which the magnetic force generation member is attached is provided on at least one of the outer surface of the communication tube portion facing the inner surface of the hole of the first member and the inner surface of the hole of the first member facing the outer surface of the communication tube portion It is formed.

  Here, it is easy to arrange the magnetic force generating member at an appropriate position by the groove.

  Preferably, in the compressor, assuming that there is no elastic member, the force required to move the valve body in contact with the valve seat away from the valve seat against the magnetic force generated by the magnetic force generating member is Assuming that there is no member, the force required to move the valve body in contact with the valve seat away from the valve seat against the force of the elastic member is five times or more and 15 times or less.

  Here, the force required to move the valve body away from the valve seat against the magnetic force generated by the magnetic force generating member is the force required to move the valve body away from the valve seat against the elastic force generated by the elastic member. Compared, more than 5 times larger. Therefore, even when the liquid refrigerant is accumulated in the pipe on the suction side when the compressor is stopped, the liquid refrigerant flows into the inside of the compressor and the oil for lubrication flows from the sliding portion. It can be suppressed.

  On the other hand, the force required to move the valve body away from the valve seat against the magnetic force generated by the magnetic force generating member is the force required to move the valve body away from the valve seat against the elastic force generated by the elastic member. 15 times or less. Therefore, when the compressor starts and the pressure in the compression chamber becomes negative, the valve body can be easily pulled away from the valve seat.

It is a schematic longitudinal cross-sectional view of the scroll compressor which concerns on one Embodiment of a compressor. It is a schematic diagram around a non-return valve mechanism for demonstrating the non-return valve mechanism with which the scroll compressor of FIG. 1 is provided. It draws the state where the suction passage is closed by the valve element of the check valve mechanism. It is a schematic diagram around a non-return valve mechanism for demonstrating the non-return valve mechanism with which the scroll compressor of FIG. 1 is provided. The drawing shows the state in which the suction path during scroll compressor operation is open. It is a schematic diagram around a non-return valve mechanism for demonstrating the non-return valve mechanism with which the scroll compressor of the modification A is equipped.

  Embodiments of a compressor will be described with reference to the drawings.

  In the following, expressions such as “upper” and “lower” may be used to explain the direction and arrangement, but unless otherwise noted, the direction of arrow U in the drawing is the upward direction.

  In addition, in the following description, expressions such as parallel, orthogonal, horizontal, vertical, and the like may be used, but these expressions are strictly related to parallel, orthogonal, horizontal, vertical, and the like. It does not mean only. The expressions such as parallel, orthogonal, horizontal, vertical, and the like include the cases of substantially parallel, orthogonal, horizontal, vertical, and the like.

(1) Overall Configuration A scroll compressor 10 according to an embodiment of the compressor will be described.

  The scroll compressor 10 according to the present embodiment is a device that compresses the refrigerant sucked from the suction port 23a in the compression chamber Sc of the compression mechanism 30, and discharges the compressed refrigerant from the discharge port 24a, as described later.

  The scroll compressor 10 is used, for example, in a vapor compression refrigeration system. In the present embodiment, the scroll compressor 10 is mounted on an outdoor unit of an air conditioner as an example of a refrigeration apparatus, and constitutes a part of a refrigerant circuit of the air conditioner. In the refrigerant circuit, the refrigerant compressed by the scroll compressor 10 dissipates heat by the radiator (condenser), is decompressed by the pressure reducing mechanism, absorbs heat by the evaporator, and is sucked again by the scroll compressor 10 Is done.

  The refrigerant to be compressed by the scroll compressor 10 is, for example, R32 of an HFC refrigerant. R32 is merely an example of the type of refrigerant, and the refrigerant to be compressed by the scroll compressor 10 may be a refrigerant other than R32.

  The scroll compressor 10 mainly includes a casing 20, a compression mechanism 30, a motor 50, a drive shaft 60, a lower bearing 70, and a check valve mechanism 80 (see FIG. 1).

(2) Detailed Configuration (2-1) Casing The scroll compressor 10 has a vertically long cylindrical casing 20. The casing 20 has a substantially cylindrical cylindrical member 21 whose upper and lower sides are open, and an upper cover 22a and a lower cover 22b provided on the upper end and the lower end of the cylindrical member 21 (see FIG. 1). The cylindrical member 21 and the upper cover 22a and the lower cover 22b are fixed by welding so as to maintain airtightness.

  The casing 20 accommodates components of the scroll compressor 10 including the compression mechanism 30, the motor 50, the drive shaft 60, the lower bearing 70, and the check valve mechanism 80.

  An oil storage space 26 is formed in the lower portion of the casing 20. The oil storage space 26 stores oil (refrigerant oil) for lubricating the sliding portion of the scroll compressor 10. The oil storage space 26 communicates with a first space S1 formed on the motor 50 side of the housing 33 of the compression mechanism 30 described later, into which the refrigerant compressed by the compression mechanism 30 flows (see FIG. 1).

  A suction pipe 23 for suctioning the refrigerant to be compressed by the compression mechanism 30 is provided in the upper portion of the casing 20 so as to penetrate the upper lid 22a (see FIG. 1). The suction pipe 23 extends upward from the casing 20 side where the suction port 23a is provided at the upper end. A refrigerant pipe 200 which constitutes a refrigerant circuit of the air conditioner together with the scroll compressor 10 is connected to the suction port 23a at the upper end of the suction pipe 23 (see FIG. 2). The refrigerant pipe 200 extends upward from the suction port 23a and then extends in a predetermined direction. The lower end of the suction pipe 23 is connected to a fixed scroll 31 of a compression mechanism 30 described later (see FIG. 1). Specifically, the suction pipe 23 is inserted and fixed in a hole 31a formed in the fixed scroll 31 (see FIG. 2). The suction pipe 23 is an example of a connecting pipe portion, and constitutes a part of a suction path 90 for guiding the refrigerant drawn from the suction port 23 a to the compression chamber Sc of the compression mechanism 30.

  The suction passage 90 includes a space communicating with the compression chamber Sc formed in the fixed scroll 31 in addition to the suction pipe 23. During operation of the scroll compressor 10, a low-pressure refrigerant before compression (a low-pressure refrigerant in the refrigeration cycle) sucked through the refrigerant pipe 200 from the suction port 23a is introduced to the compression chamber Sc. The suction passage 90 is provided with a check valve mechanism 80 described later.

  A discharge pipe 24 through which a gas refrigerant discharged to the outside of the casing 20 passes is provided at an intermediate portion of the cylindrical member 21 of the casing 20 (see FIG. 1). One end of the discharge pipe 24 is disposed outside the casing 20, and the other end of the discharge pipe 24 is disposed inside the casing 20. The end on the outer side of the casing 20 functions as the discharge port 24 a. The discharge port 24 a is connected to a refrigerant pipe (not shown) that constitutes a refrigerant circuit of the air conditioner together with the scroll compressor 10. An end of the discharge pipe 24 on the inner side of the casing 20 is disposed so as to protrude into a first space S1 formed below the housing 33 of the compression mechanism 30 described later. The high-pressure refrigerant in the refrigeration cycle after being compressed by the compression mechanism 30 is discharged to the refrigerant pipe connected to the discharge port 24a via the discharge pipe 24 and the discharge port 24a.

(2-2) Compression Mechanism The compression mechanism 30 is a mechanism for compressing the refrigerant drawn from the suction port 23a. As shown in FIG. 1, the compression mechanism 30 mainly includes a housing 33, a fixed scroll 31 disposed above the housing 33, and a movable scroll 32 which is combined with the fixed scroll 31 to form a compression chamber Sc. , (See FIG. 1).

(2-2-1) Fixed Scroll As shown in FIG. 1, the fixed scroll 31 has a substantially disc-shaped fixed side end plate 311 and a spiral fixed side projecting from the front surface (lower surface) of the fixed side end plate 311. It has a wrap 312 and a peripheral portion 313 surrounding the stationary side wrap 312.

  The fixed side wrap 312 is a wall-like member that protrudes downward (the movable scroll 32 side) from the front surface of the fixed side end plate 311. When the fixed scroll 31 is viewed from the lower side, the fixed side wrap 312 is formed in a spiral shape (involute shape) from the vicinity of the center of the fixed side end plate 311 toward the outer peripheral side.

  The fixed side wrap 312 and the movable side wrap 322 of the movable scroll 32, which will be described later, are combined to form a compression chamber Sc. The fixed scroll 31 and the movable scroll 32 are combined in a state where the front surface (lower surface) of the fixed side end plate 311 and the front surface (upper surface) of the movable side end plate 321 described later face each other. A compression chamber Sc surrounded by the movable side wrap 322 and the movable side end plate 321 of the movable scroll 32 described later is formed (see FIG. 1). As described later, when the movable scroll 32 turns relative to the fixed scroll 31, the refrigerant (low-pressure refrigerant in the refrigeration cycle) flowing from the suction passage 90 into the compression chamber Sc on the peripheral side is transferred to the compression chamber Sc on the central side. As it travels, it is compressed and the pressure rises.

  A discharge port 311a is formed substantially at the center of the fixed side end plate 311 so as to penetrate the fixed side end plate 311 in the thickness direction (vertical direction) (see FIGS. 1 and 3). The discharge port 311a communicates with the compression chamber Sc on the center side (innermost side) of the compression mechanism 30 (see FIG. 1). The high pressure refrigerant in the refrigeration cycle compressed by the compression mechanism 30 is discharged from the discharge port 311a.

  A recess 311 b (see FIG. 1) is formed on the upper surface of the fixed side end plate 311 so as to be recessed downward. The recess 311 b is formed on the upper surface of the fixed side end plate 311 in a substantially circular shape in plan view. A lid 35 is fixed to the upper surface of the fixed scroll 31 so as to close the recess 311 b (see FIG. 1). A discharge space Sa is formed between the recess 311 b and the lid 35 (see FIG. 1). The discharge space Sa communicates with the compression chamber Sc via the discharge port 311a (see FIG. 1). The high pressure refrigerant compressed in the compression chamber Sc is discharged to the discharge space Sa. The high-pressure refrigerant discharged into the discharge space Sa passes through a refrigerant passage (not shown) formed across the fixed scroll 31 and the housing 33 and flows into a first space S1 formed below the housing 33.

  The peripheral portion 313 is formed in a thick ring shape. The peripheral edge portion 313 is disposed on the outer peripheral side of the fixed side end plate 311 so as to surround the fixed side wrap 312 (see FIG. 1).

(2-2-2) Movable Scroll As shown in FIG. 1, the movable scroll 32 has a substantially disc-like movable side end plate 321 and a spiral movable side projecting from the front surface (upper surface) of the movable side end plate 321. It has a lap | wrap 322 and the cylindrical boss part 323 which protrudes from the back surface (lower surface) of the movable side end plate 321. As shown in FIG.

The movable side wrap 322 is above the front surface of the movable side mirror plate 321 (fixed scroll 31 side)
It is a wall-like member projecting to the When the movable scroll 32 is viewed from above, the movable side wrap 322 is formed in a spiral shape (involute shape) from the vicinity of the center of the movable side end plate 321 toward the outer peripheral side.

  The boss portion 323 is a cylindrical portion extending downward from the back surface of the movable side end plate 321 (see FIG. 1). The upper end of the cylinder of the boss portion 323 is closed by the movable side end plate 321. The boss portion 323 is accommodated in a crank chamber 37 described later formed by the housing 33 (see FIG. 1). A bearing metal 323a is fitted into the inside of the boss portion 323 (see FIG. 1). The eccentric portion 61 of the drive shaft 60 is inserted into the bearing metal 323a. The movable scroll 32 is connected to the drive shaft 60 by inserting the eccentric portion 61 into the boss portion 323.

(2-2-3) Housing The housing 33 is press-fit into the cylindrical member 21 and is fixed over the entire circumferential direction on the outer peripheral surface thereof. The housing 33 is disposed adjacent to the fixed scroll 31 and the movable scroll 32. The housing 33 is disposed below the fixed scroll 31 and the movable scroll 32. The housing 33 and the fixed scroll 31 are disposed such that the upper end surface of the housing 33 faces the lower surface of the peripheral edge portion 313 of the fixed scroll 31, and are fixed by a bolt or the like (not shown).

  In the housing 33, a first recess 33a disposed so as to be recessed in the upper surface central portion, an upper bearing 33c disposed below the first recess 33a, and a second recess disposed so as to surround the first recess 33a And 33b.

  The first recess 33a is formed in a circular shape in plan view. The first recess 33 a forms a crank chamber 37 therein. In the crank chamber 37, a boss portion 323 of the movable scroll 32 in which an eccentric portion 61 of a drive shaft 60 described later is inserted is disposed.

  The bearing metal 34 is fitted in the inside of the upper bearing 33c. The drive shaft 60 is inserted into the bearing metal 34. The bearing metal 34 rotatably supports the main shaft 62 of the drive shaft 60.

  The second recess 33 b is provided on the upper surface of the housing 33. The second recess 33 b is formed to surround the first recess 33 a in a plan view. The Oldham coupling 40 is disposed in the second recess 33 b.

  The Oldham coupling 40 is a member for preventing rotation of the movable scroll 32. The Oldham joint 40 includes an annular ring portion 44, a pair of key portions 42 (key portions 42 arranged approximately 180 degrees apart) extending from the ring portion 44 to the movable scroll 32 side, and a housing 33 side from the ring portion 44 And a pair of key portions (key portion 42 and key portions disposed approximately 90 degrees apart, not shown). A pair of key portions 42 extending from the ring portion 44 toward the movable scroll 32 is slidably engaged with key grooves 321 a formed on the back surface of the movable side end plate 321. One of the pair of key portions 42 of the Oldham joint 40 and a key groove 321 a with which the key portion 42 is engaged are disposed immediately below the suction path 90. A pair of key portions extending from the ring portion 44 to the housing 33 side is slidably engaged with key grooves formed on the upper surface of the housing 33. The Oldham joint 40 slidably engages with both the movable scroll 32 and the housing 33, restricts the rotation of the movable scroll 32, and revolves the movable scroll 32 relative to the fixed scroll 31.

(2-3) Motor The motor 50 drives the movable scroll 32. The motor 50 has an annular stator 51 fixed to the inner wall surface of the cylindrical member 21 and a rotor 53 rotatably accommodated inside the stator 51 with a slight gap (air gap) (see FIG. 1). ).

  The rotor 53 is a cylindrical member, and the drive shaft 60 is inserted inside. The rotor 53 is connected to the movable scroll 32 via the drive shaft 60. The motor 50 drives the movable scroll 32 by rotating the rotor 53 and turns the movable scroll 32 with respect to the fixed scroll 31.

(2-4) Drive Shaft The drive shaft 60 is disposed to extend in the vertical direction along the axial center of the cylindrical member 21, and connects the rotor 53 of the motor 50 and the movable scroll 32 of the compression mechanism 30. The drive shaft 60 transmits the driving force of the motor 50 to the movable scroll 32.

  The drive shaft 60 has a main shaft 62 whose central axis coincides with the axial center of the cylindrical member 21 and an eccentric portion 61 eccentric to the axial center of the cylindrical member 21 (the central axis of the main shaft 62) (see FIG. 1) . A refueling path 63 is formed in the drive shaft 60 (see FIG. 1).

  The eccentric portion 61 is disposed above the main shaft 62. The eccentric portion 61 is connected to the boss portion 323 of the movable scroll 32.

  The main shaft 62 is rotatably supported by a bearing metal 34 disposed in an upper bearing 33 c provided in the housing 33 and a bearing metal 71 disposed in a lower bearing 70 described later. Further, the main shaft 62 is connected to the rotor 53 of the motor 50 between the upper bearing 33 c and the lower bearing 70. The main shaft 62 rotates around a vertical axis extending in the vertical direction.

  The oil supply path 63 is an oil flow path for supplying oil to the sliding portion of the scroll compressor 10. The oil supply path 63 extends in the axial direction of the drive shaft 60 from the lower end to the upper end of the drive shaft 60 and opens at the upper and lower ends of the drive shaft 60.

  At the lower end of the drive shaft 60, an oil supply pump 65 is attached (see FIG. 1). The feed pump 65 is a positive displacement pump such as a trochoid pump. The lower end of the oil suction port 65a of the feed pump 65 is disposed in the oil storage space 26 (see FIG. 1). The discharge port of the feed pump 65 is connected to the lower end of the feed passage 63. When the drive shaft 60 rotates, the feed pump 65 is driven, and oil is sucked from the oil storage space 26 through the suction port 65 a and flows into the feed path 63. The oil that has flowed into the oil supply path 63 flows upward in the drive shaft 60. A portion of the oil flowing through the oil supply passage 63 is carried to the opening on the upper end side of the oil supply passage 63. In addition, a part of the oil flowing through the oil supply path 63 passes through a path (not shown) formed inside the drive shaft 60, and a sliding portion between the upper bearing 33 c and the drive shaft 60, the lower bearing 70 and the drive shaft 60 And the sliding part of the Further, the oil is supplied to the sliding parts of the other parts, for example, the thrust surface of the fixed scroll 31 and the movable scroll 32, the sliding part of the Oldham joint 40, and the like.

(2-5) Lower Bearing The lower bearing 70 (see FIG. 1) is disposed below the motor 50. The lower bearing 70 is fixed to the cylindrical member 21 of the casing 20. The lower bearing 70 includes a bearing metal 71 accommodated therein (see FIG. 1). The bearing metal 71 rotatably supports the lower side of the main shaft 62 of the drive shaft 60.

(2-6) Check Valve Mechanism The check valve mechanism 80 will be described with reference to FIGS. 2 and 3. FIGS. 2 and 3 are schematic views around a check valve mechanism 80 provided in the scroll compressor 10. In particular, FIG. 2 shows the suction passage 90 closed by the check valve mechanism 80, and FIG. 3 shows the suction passage 90 opened (the check valve mechanism 80 does not close the suction passage 90). ) Are drawing.

  The check valve mechanism 80 includes a valve body 82, a valve seat 84, and an elastic member 88.

  The valve body 82 is a disk-shaped member. The valve body 82 is made of a material that is attracted to the magnet, for example, a soft magnetic material. Although the material is not limited, for example, the valve body 82 is made of iron. The valve body 82 has a first position (the lowest position as shown in FIG. 3) and a second position (the highest position as shown in FIG. 2, the position pressed against the valve seat 84) along the suction path 90. And are configured to be movable.

  The valve seat 84 is a ring-shaped member fixed to the fixed scroll 31. The valve seat 84 is a member against which the valve body 82 is pressed. The valve seat 84 is disposed closer to the valve body 82 than the suction pipe 23. In other words, the suction pipe 23 is disposed closer to the suction port 23 a than the valve seat 84 in the suction passage 90. The valve seat 84 is formed in a size and shape such that the opening 84 a of the valve seat 84 through which the refrigerant passes is closed by the valve body 82 when the valve body 82 is pressed. When the valve body 82 is pressed against the valve seat 84, the suction path 90 (opening 84 a) is closed by the valve body 82.

  In the present embodiment, the valve seat 84 is a separate member from the suction pipe 23. The valve seat 84 is made of a material such as a ferrite magnet, an alnico magnet, or a rare earth magnet. The material used for the valve seat 84 may be appropriately selected based on a desired magnetic force, a desired hardness, use conditions (for example, temperature), and the like. In the present embodiment, the valve seat 84 doubles as a magnetic force generating member. The valve seat 84 as a magnetic force generation member suppresses the movement of the valve body 82 pressed against the valve seat 84 by the magnetic force.

  The elastic member 88 is a member that biases the valve body 82 toward the valve seat 84. The elastic member 88 is, for example, a spring, but an elastic member such as rubber may be used instead.

  It is preferable that the following relationship be established between the magnetic force generated by the valve body 82 and the elastic force of the elastic member 88.

  First, it is assumed that the check valve mechanism 80 does not have the elastic member 88. In this case, the force required to move the valve body 82 in contact with the valve seat 84 (sucked by the magnetic force) away from the valve seat 84 against the magnetic force generated by the valve body 82 as a magnetic force generating member. Let F1 be.

  Further, it is assumed that the check valve mechanism 80 does not have a magnetic force generating member. That is, it is assumed that the valve seat 84 of the check valve mechanism 80 is made of a material that does not generate a magnetic force. In this case, the force required to move the valve body 82 in contact with the valve seat 84 away from the valve seat 84 against the force of the elastic member 88 is represented by F2.

  At this time, it is preferable that F1 and F2 satisfy the relationship of F2 × 5 ≦ F1 ≦ F2 × 15. More preferably, it is preferable to satisfy the relationship of F1 ≧ F2 × 8.

  The advantage of the check valve mechanism 80 having both the magnetic force generating member and the elastic member is as follows.

  When the check valve mechanism 80 has only an elastic member, the elastic member 88 is pressed to press the valve body 82 strongly against the valve seat 84 in order to suppress the inflow of the liquid refrigerant accumulated above the valve body 82. It is desirable to increase the elastic force of the However, if the elastic force of the elastic member 88 is increased, a large force is required to push the valve body 82 down when the scroll compressor 10 is operated, and the efficiency may be reduced when the scroll compressor 10 is operated. On the other hand, by using the magnetic force generation member, the valve body 82 can be strongly pressed against the valve seat 84, and once the valve body 82 is separated from the valve seat 84, the valve body 82 is affected by the magnetic force. It is not received so much, and the efficiency reduction at the time of operation of scroll compressor 10 can be controlled.

  On the other hand, when the check valve mechanism 80 has only the magnetic force generation member, when the valve body 82 and the valve seat 84 are separated, almost no magnetic force acts on the valve body 82, so the scroll compression is performed. When the machine 10 is stopped, the valve body 82 may not be pressed against the valve seat 84. However, when the non-return valve mechanism 80 has an elastic member, a state in which the valve body 82 is not pressed against the valve seat 84 when the scroll compressor 10 is stopped hardly occurs.

  The movement of the valve body 82 when the scroll compressor 10 is operated and stopped will be described.

  First, during operation of the scroll compressor 10, since the refrigerant is sucked by the compression mechanism 30, the valve body 82 moves to the first position as shown in FIG. 3 by negative pressure. When the valve body 82 is disposed at the first position, the valve body 82 does not close the suction passage 90, and the refrigerant having passed through the suction port 23a flows from the outside of the scroll compressor 10 to the inside. In the first position, the magnetic force of the valve seat 84 hardly acts on the valve body 82.

  On the other hand, when the operation of the scroll compressor 10 is stopped, the pressure on the compression chamber Sc side becomes higher than the pressure on the refrigerant pipe 200 side, and the valve body 82 is pushed toward the valve seat 84 by the pressure difference. Further, when the operation of the scroll compressor 10 is stopped, the valve body 82 is moved toward the valve seat 84 by the elastic force of the elastic member 88. The elastic member 88 is configured to be able to press the valve body 82 against the valve seat 84 by an elastic force when not considering the pressure difference between the pressure on the compression chamber Sc side and the pressure on the refrigerant pipe 200 side. Is preferred. Once the valve body 82 is pressed against the valve seat 84 (moving to the second position as shown in FIG. 2), the magnetic force of the valve seat 84 suppresses the movement of the valve body 82. Particularly, as described above, even if the refrigerant is condensed and the liquid refrigerant is accumulated above the valve body 82 because F1 is larger than F2, for example, the valve body 82 is a valve seat by the magnetic force generated by the valve seat 84. It is easy to keep pressed against 84. Therefore, it is easy to suppress the occurrence of a state in which the liquid refrigerant accumulated above the valve body 82 flows in and the oil in various sliding portions in the scroll compressor 10 flows. Therefore, the occurrence of defects such as wear and seizing of the sliding portion due to insufficient lubrication is suppressed. For example, even if the key portion 42 of the Oldham joint 40 is disposed immediately below the suction path 90 as in the present embodiment, the sliding of the sliding portion due to insufficient lubrication of the key portion 42 of the Oldham joint 40 The occurrence of problems such as

  When the scroll compressor 10 is operated, the valve body 82 disposed at the second position moves to the first position as shown in FIG. 3 again.

(3) Operation of Scroll Compressor The operation of the scroll compressor 10 will be described.

  When the motor 50 is driven, the rotor 53 is rotated, and the drive shaft 60 connected to the rotor 53 is also rotated. When the drive shaft 60 rotates, the movable scroll 32 revolves with respect to the fixed scroll 31 without rotating on its own due to the function of the Oldham joint 40. Then, a low pressure (at suction pressure) refrigerant is sucked into the casing 20 through the suction pipe 23. More specifically, a low-pressure refrigerant is sucked from the suction pipe 23 to the compression chamber Sc from the peripheral side of the compression chamber Sc. As the movable scroll 32 revolves, the suction pipe 23 does not communicate with the compression chamber Sc, and as the volume of the compression chamber Sc decreases, the pressure in the compression chamber Sc increases. The pressure of the refrigerant increases as it moves from the compression chamber Sc on the peripheral side to the compression chamber Sc on the central side, and finally the pressure becomes high (discharge pressure). The high-pressure refrigerant compressed by the compression mechanism 30 is discharged into the discharge space Sa from the discharge port 311 a located near the center of the fixed side end plate 311. The high-pressure refrigerant in the discharge space Sa passes through a refrigerant passage (not shown) formed in the fixed scroll 31 and the housing 33 and flows into the first space S1 below the housing 33. The high-pressure refrigerant flowing into the first space S1 is discharged to the outside of the scroll compressor 10 from the discharge port 24a.

(4) Characteristics (4-1)
The scroll compressor 10 as an example of the compressor of the above embodiment compresses the refrigerant sucked from the suction port 23a in the compression chamber Sc and discharges it from the discharge port 24a. The scroll compressor 10 includes a suction passage 90 and a check valve mechanism 80. The suction passage 90 leads the refrigerant sucked from the suction port 23a to the compression chamber Sc. The check valve mechanism 80 is provided in the suction passage 90. The check valve mechanism 80 suppresses the backflow of the refrigerant from the inside of the scroll compressor 10 to the outside of the scroll compressor 10 through the suction port 23 a when the operation of the scroll compressor 10 is stopped. The check valve mechanism 80 includes a valve seat 84, a valve body 82, an elastic member 88, and a magnetic force generation member (valve seat 84). The valve body 82 is provided in the suction passage 90 so as to be movable along the suction passage 90 and pressed against the valve seat 84 to close the suction passage 90. The elastic member 88 biases the valve body 82 toward the valve seat 84. The magnetic force generation member suppresses the movement of the valve body 82 pressed against the valve seat 84 by the magnetic force.

  In the scroll compressor 10, the movement of the valve body 82 pressed against the valve seat 84 is suppressed by the magnetic force as well as the elastic force of the elastic member 88. The flow of the liquid refrigerant toward the interior of the scroll compressor 10 is likely to be suppressed. Therefore, in the scroll compressor 10, even when the liquid refrigerant is accumulated in the pipe on the suction side when the scroll compressor 10 is stopped, the inflow of the liquid refrigerant into the scroll compressor 10 can be suppressed, and the liquid refrigerant It is highly reliable with respect to the inflow suppression into the scroll compressor 10.

  Furthermore, in the scroll compressor 10, once the operation is started and the valve body 82 is separated from the valve seat 84, the force pressing the valve body 82 toward the valve seat 84 is only the elastic force by the elastic member 88. It is difficult to cause the performance degradation of the scroll compressor 10 due to the increase in pressure loss.

(4-2)
In the scroll compressor 10 of the above embodiment, the valve seat 84 doubles as a magnetic force generating member.

  Here, since the valve seat 84 itself is a magnetic force generating member, the movement of the valve body 82 can be relatively strongly suppressed by the magnetic force.

(4-3)
In the scroll compressor 10 of the above embodiment, the valve body 82 in contact with the valve seat 84 is separated from the valve seat 84 against the magnetic force generated by the magnetic force generating member, assuming that the elastic member 88 is not present. Force (F1) is required to move the valve body 82 in contact with the valve seat 84 away from the valve seat 84 against the force of the elastic member 88, assuming that there is no magnetic force generation member (F1). 5 times or more and 15 times or less of F2).

  Here, the force (F1) required to move the valve body 82 away from the valve seat 84 against the magnetic force generated by the magnetic force generation member opposes the elastic force generated by the elastic member 88 to the valve seat 84. Or more than five times larger than the force (F2) required to separate the Therefore, even when the liquid refrigerant is accumulated in the pipe on the suction side when the scroll compressor 10 is stopped, the liquid refrigerant flows into the scroll compressor 10 and the oil for lubrication flows from the sliding portion. It can control the occurrence of a situation.

  On the other hand, the force required to move the valve body 82 away from the valve seat 84 against the magnetic force generated by the magnetic force generating member moves the valve body 82 away from the valve seat 84 against the elastic force generated by the elastic member 88. Is less than 15 times the force required to Therefore, when the scroll compressor 10 is activated and the inside of the compression chamber Sc has a negative pressure, the valve body 82 can be easily pulled away from the valve seat 84.

(5) Modification A modification of this embodiment is shown below. A plurality of modifications may be combined appropriately as long as they do not contradict each other.

(5-1) Modification A
In the above embodiment, the valve seat 84 also functions as a magnetic force generating member, but is not limited to this.

  For example, as in the check valve mechanism 180 of FIG. 4, the valve seat 184 may be separate from the magnetic force generation member 186. The magnetic force generation member 186 is a ring-shaped magnet. The magnetic force generation member 186 does not have to be integrally formed in a ring shape, and may be formed in a ring shape by combining a plurality of divided members. When the magnetic force generation member 186 is ring-shaped, the magnetic force is particularly easily exerted on the valve body 82. However, the shape of the magnetic force generation member 186 is not limited to the ring shape, and may be locally disposed in the circumferential direction of the suction pipe 23.

  When the valve seat 84 also functions as a magnetic force generation member as in the above embodiment, an impact when the valve body 82 is pressed against the valve seat 84 or a force generated when the valve body 82 is pulled away from the valve seat 84 Thus, there is a possibility that the magnetic force generating member as the valve seat 84 may be broken.

  On the other hand, here, since the valve seat 184 is not a magnetic force generation member and the valve body 82 does not contact the magnetic force generation member 186 directly, the impact when the valve body 82 is pressed against the valve seat 184 or the valve body The force generated when 82 is pulled away from the valve seat 184 can prevent the magnetic force generating member 186 from being broken.

  In the scroll compressor shown in FIG. 4, the suction passage 90 is provided closer to the suction port 23a than the valve seat 184, and the suction pipe 23 is inserted and fixed in the hole 31a formed in the fixed scroll 31. Have. In particular, here, the valve seat 184 is an end face of the suction pipe 23 which is inserted into and fixed to the hole 31a of the fixed scroll 31 (but not limited thereto, the valve seat 184 and the suction pipe 23 are It may be separate. A groove 23c is formed on the outer surface 23b of the suction pipe 23 facing the inner surface 31b of the hole 31a of the fixed scroll 31. Note that, instead of the form shown in FIG. 4 or in addition to the form shown in FIG. 4, the magnetic force generating member 186 is provided on the inner surface 31 b of the hole 31 a of the fixed scroll 31 facing the outer surface 23 b of the suction pipe 23. A groove to be mounted may be formed.

  With this configuration, it is easy to arrange the magnetic force generation member 186 at an appropriate position with respect to the valve seat 184 by the groove.

(5-2) Modification B
In the above embodiment, the scroll compressor 10 has been described as an example of the compressor. However, the present invention is not limited to this. For example, a compressor such as a rotary compressor or a screw compressor is similar to the above embodiment. The non-return valve mechanism 180 may be employed.

(5-3) Modification C
In the above embodiment, the magnetic force generation member utilizes the magnetic force of a magnet such as a ferrite magnet, but may instead use the magnetic force of an electromagnet.

(5-4) Modification D
Although the scroll compressor 10 of the said embodiment is a vertical type scroll compressor in which the drive shaft 60 extends in the perpendicular direction, it is not limited to this. The configuration of the above embodiment may be applied to a horizontal scroll compressor in which the crankshaft of the scroll compressor extends in the horizontal direction.

  While the embodiments and modifications of the present disclosure have been described above, it is understood that various changes in form and detail can be made without departing from the spirit and scope of the present disclosure as set forth in the claims. Will.

  The present disclosure is widely applicable and useful to a compressor provided with a check valve mechanism that suppresses the backflow of the refrigerant in the suction path.

10 scroll compressor (compressor)
23 Suction pipe (communication pipe)
23a suction port 23b outer surface (outer surface of communication tube)
23c groove 24a discharge port 31 fixed scroll (first member)
31a Hole (hole formed in the first member)
31b Inner surface 80, 180 of the hole Check valve mechanism 82 Valve body 84 Valve seat (magnetic force generating member)
88 elastic member 90 suction path 184 valve seat 186 magnetic force generating member Sc compression chamber

JP, 2010-31677, A

Claims (5)

A compressor which compresses a refrigerant sucked from a suction port (23a) in a compression chamber (Sc) and discharges it from a discharge port (24a),
A suction path (90) for leading the refrigerant sucked from the suction port to the compression chamber;
A check valve mechanism (80, provided in the suction path) for suppressing the backflow of the refrigerant from the inside of the compressor to the outside of the compressor through the suction port when the operation of the compressor is stopped. 180),
Equipped with
The check valve mechanism
A valve seat (84, 184) and a valve body (82) movably provided along the suction path in the suction path and pressed against the valve seat to close the suction path;
An elastic member (88) for urging the valve body toward the valve seat;
A magnetic force generation member (84, 186) for restraining movement of the valve body pressed against the valve seat by magnetic force;
Have
Compressor (10). The valve seat (84) also functions as the magnetic force generating member,
The compressor according to claim 1. The magnetic force generation member (186) is separate from the valve seat,
The compressor according to claim 1. A first member (31) constituting a part of a compression mechanism forming the compression chamber;
The suction passage further includes a communication pipe portion (23) which is provided closer to the suction port than the valve seat and is inserted and fixed in a hole (31a) formed in the first member,
The outer surface (23b) of the communication tube portion facing the inner surface (31b) of the hole of the first member, and the inner surface of the hole of the first member facing the outer surface (23b) of the communication tube portion The groove (23c) to which the magnetic force generating member is attached is formed in at least one of (31b),
The compressor according to claim 3. If it is assumed that the elastic member is absent, the force required to move the valve body in contact with the valve seat away from the valve seat against the magnetic force generated by the magnetic force generating member is the magnetic force generating member. 5 to 15 times the force required to move the valve body in contact with the valve seat away from the valve seat against the force of the elastic member, assuming that
The compressor according to any one of claims 1 to 4.

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