JP5235962B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a scroll compressor that compresses a refrigerant used in a refrigeration cycle apparatus or the like.

2. Description of the Related Art Conventionally, a scroll compressor equipped in a refrigeration cycle apparatus such as a refrigeration, air conditioning, or hot water supply device is a compression formed by a fixed scroll housed in a hermetically sealed container and an orbiting scroll that rotates in opposition to the fixed scroll. Has a room. The compression chamber is gradually narrowed from the outer peripheral side toward the inner peripheral side by the rotation of the orbiting scroll, and the refrigerant gas is sucked and compressed from the outer peripheral side of the compression chamber, and from the central portion of the compression chamber. It is discharged into a closed container.
At this time, the fixed scroll is provided with a suction passage penetrating in the radial direction from the outer periphery of the end plate, and the suction refrigerant gas flows through the suction passage. The suction passage is constituted by two coaxial cylindrical surfaces having different inner diameters, a suction pipe is connected to the large-diameter cylindrical surface, and the small-diameter cylindrical surface (radial direction) communicates with the outer peripheral space (circumferential direction) of the compression chamber. A suction hole is provided.

A cylindrical check valve that moves while being guided by the small-diameter cylindrical surface to open and close the suction port of the suction pipe is disposed inside the small-diameter cylindrical surface. Since the check valve is biased by a spring in a direction to close the suction pipe, the suction pipe is closed when the scroll compressor is stopped.
On the other hand, when the operation of the scroll compressor is started, the refrigerant gas is discharged from the central portion of the compression chamber, and the outer peripheral side of the compression chamber becomes negative pressure. Then, the negative pressure acts on the check valve through the suction hole provided in the small-diameter cylindrical surface, and the check valve moves to the center side in the radial direction of the compressor against the biasing force of the spring. Open the opening. As a result, the refrigerant gas flows from the suction pipe through the suction passage and is sucked into the compression chamber through the suction hole (see, for example, Patent Document 1).

By the way, in the scroll compressor disclosed in Patent Document 1, the reverse phase prevention relay normally operates so that power is not supplied to the scroll compressor. That is, for example, when installing a unit such as an air conditioner, if there is a wiring mistake (so-called reverse phase that shifts the order of the phases of the three-phase power supply) to the terminal of the unit, the reverse phase prevention relay normally operates To do.
However, even if the reverse phase prevention relay is activated and the scroll compressor does not start, the scroll compressor may be forcibly started by short-circuiting the reverse phase prevention relay or removing the reverse phase prevention relay.

Then, since the scroll compressor starts in a so-called “reverse phase” in which the phase order of the three-phase power supply is shifted, the orbiting scroll performs “reverse rotation operation” that is revised in the direction opposite to the normal rotation. When the scroll compressor is continuously operated in reverse, the compression mechanism unit does not compress the refrigerant but expands the refrigerant.
Therefore, the refrigerant forcibly flows from the discharge side of the compression chamber toward the suction side (backflow from the center side toward the outer peripheral side). In this case, the refrigerant flows back from the suction hole into the small-diameter cylindrical surface, and the refrigerant flows back to the compression chamber from the suction hole by reflecting against the check valve in the small-diameter cylindrical surface.

  In this way, when the refrigerant flows backward from the suction hole into the small-diameter cylindrical surface, the spring contracts due to the backward flowing refrigerant, and the contracted spring jumps out of the suction hole together with the refrigerant and jumps into the compression chamber, and the fixed scroll and the shaking are swung. There is a case where the moving scroll is bitten. In view of this, as a countermeasure against spring pop-out, there has been proposed an integrated check valve and spring (see, for example, Patent Document 2).

However, in the invention disclosed in Patent Document 2, since the movement of the seat on the side of the anti-return valve of the spring is not restricted, when the check valve is opened, the spring is crushed and damaged by the check valve. There is a problem that the inner peripheral surface of the stop valve and the outer peripheral surface of the spring are rubbed.
In addition, there is a problem that the anti-return valve side of the spring jumps out of the suction passage (via the suction hole), enters the compression chamber, and is caught in the spiral (fixed scroll and swinging scroll).

For this reason, there is a method in which a convex portion is provided as a method for restricting the movement of the spring on the seating side.
(For example, refer to Patent Document 3).

Japanese Patent No. 4321220 (page 4-5, FIG. 2) JP 2010-127244 A (5th page, FIG. 4) JP-A-11-132164 (page 4-5, FIG. 7)

  The invention disclosed in Patent Document 3 is difficult and difficult to design and process the relationship between the suction passage and the suction hole, and is not provided in the suction hole of the scroll compressor. However, when the refrigerant is forced to flow backward as in reverse rotation operation, the spring does not pop out by providing a protrusion in the suction passage, and the spring behavior is intense, so when the check valve opens, the spring anti-return valve There is a problem that the check valve is crushed and damaged, the inner peripheral surface of the check valve and the outer peripheral surface of the spring are rubbed, and the coil of the rubbed spring is scraped and broken.

  The present invention has been made in order to solve the above-described problems. In the reverse rotation operation, the check valve spring jumps out of the suction passage, the spring is crushed by the check valve, and the check valve It is an object of the present invention to provide a scroll compressor capable of preventing the peripheral surface and the outer peripheral surface of a spring from rubbing and improving reliability.

The scroll compressor according to the present invention includes a hermetic container, a fixed scroll and an orbiting scroll that are provided in the hermetic container and meshed with each other so that a compression chamber is formed by the respective plate-like spiral teeth. A drive shaft for driving the dynamic scroll, an electric motor for driving the drive shaft, a frame that forms a compressor mechanism together with the fixed scroll and the swing scroll, a suction pipe inserted through the sealed container, wherein provided on the outer periphery side of the fixed scroll, wherein a suction passage connected suction pipe in the radial direction of the outer peripheral end, is movably disposed in the suction passage, which can close the opening of the suction pipe check valve And a spring that is installed in the suction passage and biases the check valve in the direction of the suction pipe , and a circumferential direction of the suction passage A suction port that communicates with the compression chamber, a spring seating surface that abuts one end of the spring at the radially inner peripheral end of the suction passage, and the check valve on the spring seating surface. towards protrudes a convex portion that enters the interior of the spring is formed, than the outer diameter of the end portion which abuts the check valve of the spring, the outer end abuts the spring seating surfaces of the spring who diameter rather small, the abutting ends in the check valve of the spring, characterized in that the inner curved bent portion toward the radial direction is formed.

  The scroll compressor according to the present invention includes a check valve that is movable in the suction passage, and a spring that abuts on and biases the check valve, and applies the spring shape to the check valve of the spring. The outer diameter of the end winding that abuts the spring seating surface formed in the suction passage on the anti-return valve side is smaller than the outer diameter of the end winding that comes into contact, and the convex portion provided on the spring seating surface inside the spring Is inserted into the suction passage, preventing the spring from jumping out from the suction passage when the motor is operated in reverse, and when the check valve moves to the spring seating surface, the spring seating surface side of the spring is crushed. Further, it is possible to prevent friction between the inner peripheral surface of the check valve and the outer peripheral surface of the spring, which has been conventionally generated when the check valve moves.

BRIEF DESCRIPTION OF THE DRAWINGS The longitudinal cross-sectional view explaining the structure of the scroll compressor which concerns on Embodiment 1 of this invention. The longitudinal cross-sectional view which expanded a part (near suction passage) of the scroll compressor shown in FIG. The longitudinal cross-sectional view which expanded a part (near the suction passage of a fixed scroll) of the scroll compressor shown in FIG. The longitudinal cross-sectional view which expanded a part (near suction passage) of the scroll compressor shown in FIG. The longitudinal cross-sectional view which expanded the one part (suction passage vicinity) explaining the structure of the scroll compressor which concerns on Embodiment 2 of this invention. The longitudinal cross-sectional view which expanded the one part (suction passage vicinity) explaining the structure of the scroll compressor which concerns on Embodiment 3 of this invention. The front view which extracts and shows a part (spring) of the scroll compressor which concerns on Embodiment 4 of this invention. (A) is a longitudinal cross-sectional view which shows regular installation of the spring of the scroll compressor which concerns on Embodiment 4 of this invention, (b) is a longitudinal cross-sectional view which shows incorrect installation. The longitudinal cross-sectional view which shows the state which compressed the spring of the scroll compressor which concerns on Embodiment 4 of this invention to the maximum.

[Embodiment 1: Scroll compressor]
1 to 4 illustrate the configuration of the scroll compressor according to Embodiment 1 of the present invention. FIG. 1 is a longitudinal sectional view showing the whole, and FIG. 2 is an enlarged view of a part (near the suction passage). FIG. 3 is an enlarged longitudinal sectional view of a part (near the suction passage of the fixed scroll), and FIG. 4 is an enlarged longitudinal sectional view of a part (near the suction passage). In addition, each figure is shown typically and is not limited to the shape of each constituent member or the illustrated form. Moreover, the same code | symbol is attached | subjected to the same part or an equivalent part, and one part description is abbreviate | omitted.

In FIG. 1, the scroll compressor 100 is provided with a compressor mechanism 60 and an electric motor 7 composed of a stator and a rotor in an airtight container 10.
The compressor mechanism 60 and the electric motor 7 are connected by a drive shaft 4 that transmits the rotational force generated by the electric motor 7 to the compressor mechanism 60.
The compressor mechanism 60 includes a fixed scroll 1 having a plate-like spiral tooth on one end of the end plate, a rocking scroll 2 having the same plate-like spiral tooth and a rocking bearing 2a, a compliant frame 6, and a frame 50. And.

(Inhalation passage)
In FIG. 2, a suction passage 11 is formed on the outer peripheral side of the fixed scroll 1 to guide the refrigerant to the compression chamber 1 g formed by the fixed scroll 1 and the orbiting scroll 2. A discharge port 1h for discharging the compressed refrigerant into the sealed container 10 is formed (see FIG. 1).
The suction passage 11 is formed so as to penetrate from the outer periphery of the fixed scroll 1 to the compression chamber 1 g and guide the refrigerant directly from the suction pipe 3 to the compression chamber 1 g. The suction passage 11 is formed in the radial direction from the outer periphery of the end plate of the fixed scroll 1. The cylindrical passage 12 is configured by a substantially cylindrical recess, and the suction hole 13 is formed to penetrate from the inner peripheral surface of the cylindrical passage 12 toward the outer peripheral space of the compression chamber (in the circumferential direction).

The cylindrical passage 12 has coaxial cylindrical surfaces having three different diameters, and the first cylindrical surface 1a on the open end side of the cylindrical passage 12 serves as a suction pipe connecting portion 12a, and the second cylindrical surface 1b and the third cylinder. The surface 1c becomes the check valve sliding portion 12b. The first cylindrical surface 1a and the second cylindrical surface 1b are configured to have a smaller inner diameter in this order.
In FIG. 3, a cylindrical passage 12 includes a check valve sliding portion 12b (second cylindrical surface 1b and third cylindrical surface 1c) and a spring seating surface 1d that closes an end surface of the third cylindrical surface 1c in the axial direction of the cylindrical surface. And a cylindrical convex portion 1e protruding toward the check valve 14 provided on the spring seating surface 1d.

(Check valve / spring)
The suction pipe 3 inserted through the sealed container 10 is connected to the suction pipe connection portion 12a. Further, the check valve 14 and the spring 15 are accommodated in the check valve sliding portion 12b.
The check valve 14 is movable while being guided by the second cylindrical surface 1b, and has a cup shape for preventing a reverse flow of the refrigerant.
One end of the spring 15 contacts the spring seating surface 1d in the suction passage 11, and the other end enters the check valve (cup) 14 from the open end 14c and contacts the inner surface (bottom surface of the cup) 14b. The check valve 14 is urged in a direction to close the opening of the suction pipe 3. The spring 15 has a tapered shape, and is attached to the outer periphery of the convex portion 1e with the smaller-diameter end (hereinafter referred to as "seat surface side") 15b having a smaller outer shape facing the spring seat surface 1d.

In the check valve sliding portion 12b configured as described above, the check valve 14 presses (compresses) the spring 15 against its biasing force during the forward rotation operation of the compressor, and the suction pipe 3 Release the blockage. As a result, the suction passage 11 and the suction pipe 3 communicate with each other, and the refrigerant is sucked from the suction pipe 3 into the cylindrical passage 12 of the suction passage 11 and further sucked into the compression chamber 1g through the suction hole 13.
On the other hand, when the compressor is stopped, the check valve 14 closes the opening of the suction pipe 3 by the biasing force of the spring 15 to prevent the refrigerant from flowing backward.

(Operation: Normal operation)
Next, the operation will be described. When the operation of the scroll compressor 100 is started, the compression chamber 1g becomes negative pressure and takes in the suction refrigerant gas. At this time, this negative pressure acts on the check valve 14 via the suction hole 13 and the cylindrical passage 12, and the check valve 14 resists the urging force of the spring 15 to the center side in the radial direction of the scroll compressor 100. Moving.
As a result, the suction pipe 3 is closed, the suction pipe 3 and the suction passage (the cylindrical passage 12 and the suction hole 13) communicate, and the refrigerant gas is sucked into the sealed container 10 from the suction pipe 3. The refrigerant gas flows into the outer peripheral portion (compression chamber outer peripheral space 1i) of the compression chamber 1g through the suction passage 11 (the cylindrical passage 12 and the suction hole 13). Thereafter, the refrigerant gas is compressed by the electric motor 7 using the rotational force applied through the drive shaft 4, and enters the sealed container 10 through the discharge port 1 h formed at the center of the fixed scroll 1 in a high pressure state. Discharged.
The high-pressure refrigerant gas discharged into the hermetic container 10 fills the hermetic container 10 with a high-pressure atmosphere, and this high-pressure refrigerant gas passes through the discharge pipe 5 provided in the body of the hermetic container 10. 10 is discharged outside.

Lubricating oil 10a is stored at the bottom of the sealed container 10, and the lower end of the drive shaft 4 is immersed in the lubricating oil 10a. An oil supply hole 4a is provided at the center of the drive shaft 4, and the bottom of the sealed container 10 communicates with the compression chamber outer peripheral space 1i through the oil supply hole 4a, the rocking bearing 2a, and the main bearing 6a.
During the operation of the scroll compressor 100, the inside of the sealed container 10 is filled with a high pressure atmosphere, so that the lubricating oil 10a rises in the oil supply hole 4a by the pressure difference from the low pressure atmosphere of the sucked refrigerant gas and becomes an orbiting scroll 2. The rocking bearing 2a provided and the main bearing 6a provided on the compliant frame 6 are lubricated and then guided to the outer circumferential space 1i of the compression chamber.

(Operation: Reverse operation)
Next, the effect | action by the structure of the characteristic part of Embodiment 1 of this invention is demonstrated. In the scroll compressor 100 configured as described above, when a three-phase or single-phase induction motor is used for the electric motor 7, in the assembly of a unit (for example, an air conditioner), the operating capacitor of the three-phase induction motor Due to a connection mistake or the like, the electric motor 7 may be rotated in reverse during the production line test.
In the case of a brushless DC motor driven by an inverter, a normal drive circuit (not shown) has a built-in protection circuit that detects the reverse phase of the power supply and cuts off the power to the brushless DC motor. If there is a connection error of the power supply terminal to the glass terminal 16 (see FIG. 1), the scroll compressor 100 does not start. However, if the drive circuit does not have a built-in protection circuit that detects the reverse phase of the power supply and shuts off the power to the brushless DC motor, the scroll compressor will reverse if there is a connection error in the power supply terminal to the scroll compressor. There is a case.

In the connection of the three-phase induction motor, if the three power terminals (U-phase, V-phase, W-phase) are correctly connected to the glass terminal 16 (see FIG. 1) of the scroll compressor, the electric motor 7 can be operated in a predetermined forward direction. I do. However, for example, if the connection between the U phase and the V phase is wrong (the V phase of the power supply is connected to the U phase winding and the U phase of the power supply is connected to the V phase winding), the electric motor 7 moves in a predetermined direction. It rotates in the opposite direction to the forward rotation that rotates (reverse rotation).
In connection with a single-phase induction motor, usually, an operating capacitor is connected in series to the auxiliary winding, and the series circuit is connected in parallel to the main winding. If the operating capacitor is connected to the main winding and the series circuit is connected in parallel to the auxiliary winding due to a connection error of the operating capacitor, the motor 7 is in the opposite direction to the forward rotation that rotates in a predetermined direction. Performs reverse rotation that rotates.

Next, a description will be given of a reverse rotation operation due to a connection mistake at the time of installation of an air conditioner (not shown) including an outdoor unit on which the scroll compressor 100 is mounted and an indoor unit. In this case, the scroll compressor 100 using a three-phase induction motor for the electric motor 7 is an object.
If the motor 7 is a brushless DC motor driven by an inverter, the drive circuit does not have a built-in protection circuit that detects the reverse phase of the power supply and cuts off the power to the brushless DC motor. In the connection of the three-phase power supply to the power supply connection terminal, if the phase order is shifted, the electric motor of the scroll compressor performs a reverse operation.
Further, in the case of a scroll compressor that uses a single-phase induction motor for the electric motor 7, even if the phase (two-phase) order is shifted in the connection of the single-phase power supply to the power supply connection terminal of the outdoor unit during installation, the electric motor 7 does not occur, but when the operating capacitor is serviced (replaced) after installation, a reverse operation occurs due to a connection error.

In the above case, when the scroll compressor 100 is operated in reverse, the refrigerant is forced to flow backward from the discharge side to the suction side. At this time, the refrigerant flows from the suction hole 13 toward the cylindrical passage 12 and hits the spring 15. The spring 15 moves or contracts in the cylindrical passage 12 of the suction passage 11 due to the flow of the refrigerant. However, since the convex portion 1e inserted inside the spring 15 is provided, the movement of the spring 15 is prevented. Thus, the spring 15 is prevented from being detached from the suction passage 11. As a result, it is possible to eliminate the inconvenience that the spring 15 is disengaged from the suction passage 11 in an abnormal mode such as reverse phase operation. Therefore, it is possible to resume normal operation by returning to the normal power supply connection state after the reverse phase is released, and a highly reliable scroll compressor can be obtained.
However, when the spring 15 has a straight shape, the spring 15 repeatedly expands and contracts violently and rapidly at the time of the reverse flow of the refrigerant, so that the spring 15 does not come off. Therefore, the outer periphery of the attached spring 15 and the inner periphery of the check valve 14 The surface is rubbed, and the wire forming the coil of the spring 15 is scraped or worn, causing a phenomenon that the wire is broken, that is, the spring 15 is broken. Therefore, the spring 15 is tapered to prevent these phenomena.

In FIG. 4, the shape of the spring 15 is a taper shape, and the code | symbol which shows a dimension means the following.
doa: outer diameter of the check valve side 15a of the spring 15,
dob: outer diameter of the seating surface side 15b of the spring 15,
dia: inner diameter of the check valve side 15a of the spring 15,
dib: inner diameter of the seating surface side 15b of the spring 15,
Di: inner diameter of check valve 14,
Do: outer diameter of the convex portion 1e,
H: height of the convex part 1e,
h: Cup depth of the check valve 14.
And it has the characteristics in the point which set it as the structure where the relationship of each dimension satisfy | fills both Formula 1 and Formula 2. FIG.
(Di-doa) <(Di-dob) (Equation 1)
(Dib-Do) <(Di-dob) (Equation 2)

Further, “h” is the cup depth of the check valve 14, that is, the check valve 14 has a cup shape in which one end is closed by the closing plate 14 a (corresponding to the cup bottom), and therefore the inner surface 14 b of the closing plate 14 a. This corresponds to the distance (corresponding to the inner surface of the cup bottom) to the open end 14c (the axial length of the internal space of the check valve 14).
The height “H” of the convex portion 1 e is characterized in that it is equal to or higher than the height at which one turn of the spring 15 is caught while the check valve 14 is closed, and the structure satisfies Expression 3.
H <h (Formula 3)

In this manner, the scroll compressor 100 has a cylindrical shape that protrudes in the expansion and contraction direction of the spring 15 and is inserted into the spring 15 on the spring seating surface 1d of the suction passage 11 in a tapered shape. 1e is provided, and the dimensional relationship of the above-mentioned formulas 1 to 3 is satisfied, so that the spring 15 is prevented from abruptly moving during the reverse rotation operation, and the shape of the spring 15 is tapered so as to satisfy the formulas 1 and 2. This prevents the spring 15 from being damaged by rubbing between the inner peripheral surface of the check valve 14 and the outer peripheral surface of the spring 15, or prevents the seating side of the spring 15 from being crushed by the check valve 14. be able to. Further, by adopting this tapered shape, the inner peripheral surface of the spring 15 is not rubbed with the outer peripheral surface of the cylindrical convex portion 1e, so that the spring 15 can be prevented from being damaged and can be expanded and contracted smoothly. That is, during normal operation, even if the check valve 14 operates, there is no need to counteract the force (friction force) that the spring 15 rubs against the inner peripheral surface of the check valve 14 or the outer peripheral surface of the convex portion 1e. Since it can be sufficiently operated only by the urging force of the spring 15, it is possible to suppress generation of useless force.
Further, the inner peripheral surface of the check valve 14 and the outer peripheral surface of the spring 15 are not rubbed, or the inner peripheral surface of the spring 15 and the outer peripheral surface of the cylindrical convex portion 1e are not rubbed. Even without using high-priced, expensive wires or wires with complicated and expensive surface treatments such as plating and coating, it is possible to ensure a longer spring life with cheap materials and wires using processing methods. It is possible to obtain a more reliable product even when used for a long time.
In addition, although the cylindrical convex part 1e is demonstrated by the cylindrical shape of the same outer diameter from the spring seating surface 1d to the front-end | tip of the convex part 1e, the outer diameter of the convex part 1e does not necessarily need to be the same. . For example, a tapered cylindrical shape having a small diameter on the spring seating surface 1d side may be used. By doing so, the spring 15 is less disengaged from the convex portion 1e. Further, there may be a groove in which the end winding portion of the spring 15 is locked at the connection portion between the spring seating surface and the convex portion 1e, and the end portion of the spring 15 may be locked. Similar to the shape of the convex portion 1e, the spring 15 is unlikely to be detached from the convex portion 1e. The groove width at that time is the same as the wire rod diameter of the spring 15, and the depth should be 50% or more of the wire rod diameter of the spring 15. That is, when the wire rod is fitted to the groove by 50%, the wire rod diameter of the spring 15 is pressed by the width of the groove, so that the effect of locking the spring end winding portion is sufficiently obtained.
Further, the end portion of the spring 15 may be in contact with or fixed to the inside of the side surface of the check valve 14 in addition to being in contact with or fixed to the inner surface 14b of the closing plate 14a of the check valve 14. In other words, the diameter of the end winding portion of the spring 15 is slightly larger than the inner peripheral diameter of the check valve 14 and the force of spreading the end winding portion is used as a side pressure to stop the contact diameter against the side portion of the check valve 14. Absent. Since the spring 15 is tapered, the other part of the spring does not contact the side surface of the check valve 14 even if the spring 15 is expanded or contracted. Therefore, the coil of the spring 15 is not scraped off or worn. Of course, you may latch in the form hold | maintained to both the side part of the non-return valve 14, and the inner surface 14b of the obstruction board 14a.
As described above, it is possible to resume normal operation by returning to the normal power supply connection state after canceling the reverse rotation operation, and the highly reliable scroll compressor 100 can be obtained.

[Embodiment 2]
FIG. 5 is an enlarged longitudinal sectional view illustrating a part of the scroll compressor according to Embodiment 2 of the present invention (part of the vicinity of the suction passage). In addition, each figure is shown typically and is not limited to the shape of each constituent member or the illustrated form. In addition, the same reference numerals are given to the same or corresponding parts as in the first embodiment, and a part of the description is omitted.

In FIG. 5, the scroll compressor 200 has a spring 17 that is a combination of two cylindrical springs having different outer diameters that are easier to process than the tapered spring 15 of the scroll compressor 100. .
That is, the spring 17 includes several turns of the check valve side cylindrical spring portion (large diameter portion) 17a and several turns of the seating surface side cylindrical spring portion (outer diameter smaller than the inner diameter of the check valve side cylindrical spring portion 17a). Small diameter portion) 17b. Therefore, similarly to the spring 15, the seating surface side 17 b of the spring 17 can be prevented from being crushed by the check valve 14, and rubbing between the inner peripheral surface of the check valve 14 and the outer peripheral surface of the spring 17 can be prevented.

The shape of the spring 17 is a combination of the check valve side cylindrical spring portion 17a and the seating surface side cylindrical spring portion 17b, and the symbols indicating the dimensions mean the following.
doa: outer diameter of the checker side cylindrical spring portion 17a of the spring 17,
dob: outer diameter of the seating surface side cylindrical spring portion 17b of the spring 17,
dia: inner diameter of the check valve side cylindrical spring portion 17a,
dib: inner diameter of the seating surface side cylindrical spring portion 17b,
Di: inner diameter of check valve 14,
Do: outer diameter of the convex portion 1e,
La: Length of the check valve side cylindrical spring portion 17a of the spring 17 in a state where the check valve 14 is closed,
Lb: length of the seating surface side cylindrical spring portion 17b in the state where the check valve 14 is closed,
H: height of the convex part 1e,
h: Distance between the inner surface 14b of the closing plate 14a of the check valve 14 and the open end 14c of the check valve 14 (the axial length of the internal space of the check valve 14).
And each dimension has the relationship of Formula 4-6.
(Di-doa) <(Di-dob) (Formula 4)
(Dib-Do) <(Di-dob) (Formula 5)
La ≦ h (Formula 6)
Further, the height H of the convex portion 1e is equal to or higher than the height at which one turn of the seating surface side cylindrical spring portion 17b of the spring 17 is caught in the state where the check valve 14 is closed, and the dimensional relationship of the formula H <h. It is characterized in that it has a structure satisfying the above.
H <h (Formula 7)
As a result, an effect equivalent to that of a spring having a tapered shape can be obtained by a spring that can be manufactured by an inexpensive design process.
As described above, after canceling the reverse rotation operation, it is possible to resume the normal operation by returning to the normal power supply connection state, and a highly reliable scroll compressor can be obtained.

[Embodiment 3]
FIG. 6 is an enlarged longitudinal sectional view of a part (near the suction passage) for explaining the configuration of the scroll compressor according to Embodiment 3 of the present invention. In addition, each figure is shown typically and is not limited to the shape of each constituent member or the illustrated form. In addition, the same reference numerals are given to the same or corresponding parts as in the first embodiment, and a part of the description is omitted.

In FIG. 6, the scroll compressor 300 has a tapered spring 18 instead of the spring 15 of the scroll compressor 100.
The contact height of the spring 18 is “Hs”, which is smaller than the cup depth “h (distance from the inner surface 14b of the closing plate 14a to the open end 14c)” of the check valve 14. That is, Expression 8 is satisfied.
Hs <h (Formula 8)

Here, the contact height Hs is the height of the entire spring 18 in a state in which the spring 18 is compressed and the coils are in contact with each other. When the spring 18 is pressed to the contact height Hs, excessive stress is generated in the spring 18.
In FIG. 6, when the check valve 14 is pressed to the maximum against the urging force of the spring 15, the open end 14 c of the check valve 14 abuts against the spring seating surface 1 d, so that the space for accommodating the spring 18 The length is the depth “h” of the check valve 14 cup. That is, when the spring 18 is most compressed, the spring 18 contracts to this length “h”.
Therefore, if the length h in the spring accommodating space is shorter than the contact height Hs of the spring 18, excessive stress is generated in the spring 18, and if such pressing is repeated for a long time, the spring 18 Although there is a risk of breakage, since the scroll compressor 300 is configured to satisfy Equation 8, the spring 18 does not shrink to the contact height Hs, and contact (pressing) between the coil wires is prevented. The That is, the coil wires can be prevented from being damaged.
In addition, since the coil wires will not be damaged each other, it is not necessary to use expensive wires with high durability and wires with complicated and expensive surface treatments such as plating and coating to protect the surface of the wires. In addition, it is possible to ensure a longer life of the spring than a conventional coil by using an inexpensive material or a wire made by a processing method, and a more reliable one can be obtained even when used for a long time.

Next, the effect | action by the structure of the characteristic part of the scroll compressor 300 is demonstrated. The operation of the compression mechanism is the same as that of the scroll compressor 100 (Embodiments 1 and 2).
During operation of the scroll compressor 300, the refrigerant gas flows through the suction passage 11, and the check valve 14 is pressed in a direction against the urging force of the spring 18. At this time, even when the check valve 14 is pressed to the maximum and the open end 14c of the check valve 14 is in contact with the spring seating surface 1d, the spring 18 does not contract to the contact height Hs.
As described above, in the scroll compressor 300, between the spring seating surface 1d and the check plate 14a of the check valve 14 in a state where the check valve 14 is pressed to the maximum in the direction against the urging force of the spring 18. Since the distance h is configured to be larger than the contact height Hs of the spring 18, excessive stress is not generated in the spring 18, and even when the spring 18 contracts to the contact height, the coil wires contact and press each other. Thus, it is possible to obtain the scroll compressor 100 having higher reliability than those of the first and second embodiments, which can prevent the spring 18 from being damaged during long-term use without damaging or damaging the wire.

[Embodiment 4]
FIGS. 7 to 9 illustrate the configuration of the scroll compressor according to Embodiment 4 of the present invention. FIG. 7 is a front view showing a part (spring) extracted, and FIG. FIG. 8B is a longitudinal sectional view showing incorrect installation of the spring, and FIG. 9 is a longitudinal sectional view showing a state where the spring is compressed to the maximum. In addition, each figure is shown typically and is not limited to the shape of each constituent member or the illustrated form. In addition, the same reference numerals are given to the same or corresponding parts as in the first embodiment, and a part of the description is omitted.

In FIG. 7, the scroll compressor 400 has a spring 19 instead of the spring 15 of the scroll compressor 100.
The spring 19 is bent at the end of the check valve side 19a on the inner side (center axis side), and a linear bent portion 19c continuous with the end of the winding is formed.
Therefore, when the spring 19 is installed in the normal posture shown in FIG. 8A, the anti-return valve side 19b of the spring 19 is inserted into the convex portion 1e. On the other hand, if an attempt is made to install the spring 19 in the wrong posture shown in FIG. 8B, the bent portion 19c formed on the check valve side 19a of the spring 19 rides on (abuts) the top of the convex portion 1e. The spring 19 cannot be installed on the convex portion 1e.
Therefore, according to the spring 19, the problem of installing upside down is solved.

Also, as shown in FIG. 9, when the outer diameter of the wire forming the spring 19 (same as the outer diameter of the bent portion 19c) is “e”,
e <(h−H) (Equation 9)
There is a relationship.
Therefore, even when the check valve 14 is pushed in to the maximum (the open end 14c of the check valve 14 is in contact with the spring seating surface 1d), the bent portion 19c of the spring 19 is connected to the convex portion 1e and the check valve. 14 and is not damaged.
In the above, the bent portion is formed for the spring 15 in the first embodiment, but the present invention is not limited to this, and the bent portions are formed in the springs 17 and 18 in the second and third embodiments. May be.
As described above, it is possible to construct a scroll compressor with few assembling errors even when the compressor is assembled, and it is possible to obtain high reliability even during operation in which the spring is not damaged even when the check valve is pushed to the maximum. A highly efficient scroll compressor can be obtained.

  1: fixed scroll, 1a: first cylindrical surface, 1b: second cylindrical surface, 1c: third cylindrical surface, 1d: spring seating surface, 1e: convex portion, 1g: compression chamber, 1h: discharge port, 1i: compression Outer chamber space, 2: oscillating scroll, 2a: oscillating bearing, 3: suction pipe, 4: drive shaft, 4a: oiling hole, 5: discharge pipe, 6: compliant frame, 6a: main bearing, 7: electric motor 10: Airtight container, 10a: Lubricating oil, 11: Suction passage, 12: Cylindrical passage, 12a: Suction pipe connecting portion, 12b: Check valve sliding portion, 13: Suction hole, 14: Check valve, 14a: Blocking plate, 14b: inner surface, 14c: open end, 15: spring (Embodiment 1), 15a: check valve side, 15b: seating surface side, 16: glass terminal, 17: spring (Embodiment 2), 17a: Check valve side cylindrical spring portion, 17b: Seating surface Cylindrical spring part, 18: Spring (Embodiment 3), 19: Spring (Embodiment 4), 19a: Check valve side, 19b: Anti-check valve side, 19c: Bent part, 50: Frame, 60: Compression 100: Scroll compressor (Embodiment 1), 200: Scroll compressor (Embodiment 2), 300: Scroll compressor (Embodiment 3), 400: Scroll compressor (Embodiment 4) ), Di: Check valve inner diameter, Do: Convex outer diameter, dia: Check valve side cylindrical spring inner diameter, dib: Seating surface side cylindrical spring inner diameter, doa: Check valve side cylindrical spring outer diameter, dob : Seating surface side cylindrical spring part outer diameter, e: Spring wire diameter, h: Axial length of the inner space of the check valve, H: Convex part height, Hs: Adhesion height.

Claims (3)

A sealed container;
A fixed scroll and an orbiting scroll provided in the sealed container and meshed with each other so that a compression chamber is formed by each plate-like spiral tooth;
A drive shaft for driving the orbiting scroll and an electric motor for driving the drive shaft;
A frame constituting a compressor mechanism together with the fixed scroll and the swing scroll;
A suction pipe inserted through the sealed container;
A suction passage provided near the outer periphery of the fixed scroll, wherein the suction pipe is connected at a radially outer peripheral end;
A check valve movably disposed in the suction passage and capable of closing the opening of the suction pipe;
A spring installed in the suction passage and biasing the check valve in the direction of the suction pipe,
A suction port communicating with the compression chamber on a side surface in a circumferential direction of the suction passage; a spring seating surface on which one end of the spring abuts on a radially inner peripheral end of the suction passage; and the spring A protruding portion that protrudes toward the check valve on the seating surface and enters the inside of the spring is formed,
Said than the outer diameter of the abutting ends on the check valve spring, towards the outer diameter of the abutting ends in the spring seating surface of the spring rather small,
A scroll compressor characterized in that a bent portion that is bent inward in the radial direction is formed at an end of the spring that contacts the check valve .   2. The scroll compressor according to claim 1, wherein the outer diameter of the spring changes smoothly from one end portion to the other end portion or changes stepwise. The check valve is a bottomed cylinder having one end opened and the other end closed by a closing plate;
The scroll compressor according to claim 1 or 2, wherein a distance between the open end and the closing plate is larger than a contact height of the spring.

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