KR101302890B1 - Scroll compressor - Google Patents

Abstract

[assignment]
It is possible to prevent the spring of the check valve from protruding from the suction passage during the reverse operation, to prevent the spring from being crushed by the check valve, and to rub the inner circumferential surface of the check valve and the outer circumferential surface of the spring, thereby improving reliability. Provide a scroll compressor.
[Solution]
Spring 15 provided in scroll compressor 100 (outer diameter doa of check valve side 15a, outer diameter dob of seating surface side 15b, inner diameter dia of check valve side 15a, inner diameter dib of seating surface side 15b) And check valve 14 (inner diameter Di, outer diameter Do, cup depth h) satisfy | fill Equation 1, 2, and satisfy | fill Equation 3 between height H of the convex part 1e provided in the suction path 11. .
(Di-doa) <(Di-dob)... ... (Equation 1)
(dib-Do) <(Di-dob)... ... (Equation 2)
H <h… ... (Equation 3)

Description

[0001] SCROLL COMPRESSOR [0002]

The present invention relates to a scroll compressor for compressing a refrigerant used in a refrigeration cycle device or the like.

BACKGROUND ART Conventionally, a scroll compressor equipped with a refrigeration cycle apparatus such as a refrigeration, air conditioning, or hot water supply equipment has a compression chamber formed by a fixed scroll housed in an airtight container and a swinging scroll rotating against the fixed scroll. Have The compression chamber is narrowed gradually from the outer circumference side to the inner circumference side by rotation of the swinging scroll. The refrigerant gas is sucked from the outer circumference side of the compression chamber and compressed, and is discharged from the center of the compression chamber into the sealed container.

At this time, the fixed scroll is provided with a suction passage penetrating in the radial direction from the outer periphery of the hard plate, and the suction refrigerant gas is introduced through the suction passage. The suction passage is composed of a coaxial cylindrical surface composed of two different inner diameters, the suction pipe is connected to a large diameter cylindrical surface, and the suction passage communicates with the outer peripheral space (circumferential direction) of the compression chamber to the small diameter cylindrical surface (radial direction). A hole is provided.

And inside the cylindrical surface of a small diameter, the cylinder type check valve which is guided and moves in the cylindrical surface of a small diameter, and opens and closes the suction port of a suction pipe is arrange | positioned. Since the check valve is biased by a spring in the direction of closing the suction pipe, the suction pipe is closed when the scroll compressor is stopped.

On the other hand, when the scroll compressor starts to operate, the refrigerant gas is discharged from the center 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 cylindrical surface of the small diameter, the check valve moves to the center side in the radial direction of the compressor against the force of the spring, and opens the opening of the suction pipe. As a result, the refrigerant gas flows in from the suction pipe through the suction passage and is sucked into the compression chamber via the suction hole (see Patent Document 1, for example).

By the way, in the scroll compressor disclosed in Patent Document 1, a reverse phase prevention relay is usually operated so that power is not supplied to the scroll compressor. That is, for example, when passing through a unit such as an air conditioner, if there is a wiring error to the terminal of the unit (so-called reverse phase where the phase of the three-phase power source is out of order), the reverse phase is usually reversed. The protection relay is activated.

However, even when the anti-phase relay operates and the scroll compressor does not start, the anti-phase relay may be forcibly started by removing the short circuit or the anti-phase relay from the anti-phase relay.

Then, since the scroll compressor starts in the so-called "reverse phase" in which the phases of the three-phase power source are out of order, the swing scroll performs "reverse operation" which rotates in the direction opposite to the forward rotation. When the scroll compressor is continuously inverted and operated, the compression mechanism unit is operated to expand the refrigerant rather than compress the refrigerant.

Therefore, the refrigerant flows forcibly from the discharge side of the compression chamber toward the suction side (flows back from the center side toward the outer circumferential side). In this case, the refrigerant flows back from the suction hole into the cylindrical surface of the small diameter, touches the check valve in the cylindrical surface of the small diameter, reflects it, and this time a flow of the refrigerant returns from the suction hole to the compression chamber.

In this way, when the refrigerant flows back from the suction hole into the cylindrical surface of the small diameter, the spring contracts due to the refrigerant flowing back, and the spring that contracts springs out of the suction hole together with the refrigerant and enters the compression chamber, thereby fixed scroll and swinging scroll. It may be interlocked. Therefore, as a countermeasure against spring sticking out, it has been proposed to integrate a check valve and a spring (see Patent Document 2, for example).

However, in the invention disclosed in Patent Document 2, since the movement of the seating side, which is the anti-return valve side of the spring, is not regulated, the spring is crushed by the check valve when the check valve is opened, and the check There is a problem that the inner circumferential surface of the valve and the outer circumferential surface of the spring are rubbed.

In addition, there is a problem that the half-return valve side of the spring protrudes from the suction passage (via the suction hole), enters the compression chamber, and engages with the scrolls (fixed scroll and swinging scroll).

For this reason, some convex parts are provided as a method of restricting the movement of the spring on the seating side. (See, for example, Patent Document 3).

[Patent Document]

Patent Document 1: Japanese Patent No. 4312220 (Pages 4 to 5, Fig. 2)

Patent Document 2: Japanese Patent Application Laid-Open No. 2010-127244 (No. 5 page, Fig. 4)

Patent Document 3: Japanese Patent Application Laid-Open No. 11-132164 (pages 4 to 5, FIG. 7)

The invention disclosed in Patent Literature 3 is difficult and difficult to design and process the relationship between the suction passage and the suction hole, and thus is not provided in the suction hole of the scroll compressor. However, when the refrigerant flows back in force, such as in reverse operation, even if the spring does not protrude by providing a convex portion in the suction passage, the behavior of the spring is severe. Therefore, when the check valve is opened, the counter valve side of the spring is connected to the check valve. There is a problem of being crushed and broken, rubbing the inner circumferential surface of the check valve and the outer circumferential surface of the spring, and shaping and bending the coil of the rubbed spring.

SUMMARY OF THE INVENTION The present invention has been made to solve the problems as described above, wherein the spring of the check valve springs out of the suction passage during reverse operation, the spring is crushed by the check valve, and the inner circumferential surface of the check valve and the spring It is to provide a scroll compressor which can prevent the outer peripheral surface from being rubbed and can improve the reliability.

In the scroll compressor according to the present invention, a check valve free to move in a suction passage and a spring that abuts against the check valve and are added thereto are disposed, and the spring is smaller than the outer diameter of the left winding part which abuts against the check valve of the spring. The outer diameter of the left turn which abuts against the spring seating surface on the half-return valve side has a small shape, and the convex portion formed on the spring seating surface is inserted into and attached to the inside of the spring.

In the scroll compressor according to the present invention, a check valve free to move in the suction passage and a spring that abuts against the check valve and are added thereto are disposed, and the spring shape is smaller than the outer diameter of the left turn that contacts the check valve of the spring. Since the outer diameter of the left turn contacting the spring seating surface formed in the suction passage in the suction passage is small, and the convex portion provided on the spring seating surface is inserted into the spring and attached to the suction passage, Protruding from the spring intake passage is prevented, when the check valve is moved to the spring seating surface side, the spring seating surface side of the spring is prevented from crushing, and the inner circumferential surface of the check valve that has conventionally been generated when the check valve is moved. Rubbing of the outer circumferential surface of the spring can be prevented.

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.
FIG. 2 is an enlarged longitudinal sectional view of a part (near the suction passage) of the scroll compressor shown in FIG. 1; FIG.
3 is an enlarged longitudinal sectional view of a part of the scroll compressor shown in FIG. 1 (near the suction passage of the fixed scroll);
FIG. 4 is an enlarged longitudinal sectional view of a part (near the suction passage) of the scroll compressor shown in FIG. 1. FIG.
FIG. 5 is an enlarged longitudinal sectional view for explaining a configuration of a scroll compressor according to a second embodiment of the present invention, in the vicinity of a suction passage; FIG.
FIG. 6 is an enlarged longitudinal sectional view for explaining a configuration of a scroll compressor according to a third embodiment of the present invention (near the suction passage). FIG.
Fig. 7 is a front view showing a part of the scroll compressor (spring) taken out according to Embodiment 4 of the present invention.
8 is a longitudinal sectional view showing (a) normal installation, and (b) a longitudinal sectional view showing incorrect installation of the spring of the scroll compressor according to Embodiment 4 of the present invention.
9 is a longitudinal sectional view showing a state in which the spring of the scroll compressor according to the fourth embodiment of the present invention is compressed as much as possible.

Embodiment 1: Scroll Compressor

1 to 4 illustrate the structure of the scroll compressor according to the first embodiment of the present invention, in which FIG. 1 is a longitudinal sectional view showing the whole, and FIG. 2 is a longitudinal sectional view in which a part (near the suction passages) is enlarged. 3 is a longitudinal cross-sectional view which enlarged a part (near the suction passage of a fixed scroll), and FIG. 4 is a longitudinal cross-sectional view which enlarged a part (near a suction passage). In addition, each figure is shown typically, and is not limited to the shape of each structural member, or the form to show in figure. In addition, the same code | symbol is attached | subjected to the same part or corresponding part, and the description of a part is abbreviate | omitted.

In FIG. 1, in the scroll compressor 100, a compressor mechanism 60, an electric motor 7 composed of a stator and a rotor are disposed in the sealed container 10.

The compressor mechanism 60 and the electric motor 7 are connected by the drive shaft 4 which transmits the rotational force which the electric motor 7 produces to the compressor mechanism 60.

The compressor mechanism part 60 has a fixed scroll 1 having a plate-shaped spiral tooth on one side of the hard plate, and a plate-shaped vortex and swing bearing 2a of the same shape. A rocking scroll 2, a compliant frame 6, and a frame 50 are provided.

(Suction passage)

In Fig. 2, on the outer circumferential side of the fixed scroll 1, a suction passage 11 for guiding the refrigerant into the compression chamber 1g formed by the fixed scroll 1 and the swinging scroll 2 is formed, and the fixed scroll At the center of (1), 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 through the compression chamber 1g from the outer circumference of the fixed scroll 1 to guide the refrigerant directly from the suction pipe 3 to the compression chamber 1g, and the fixed scroll 1 A cylindrical passage 12 composed of a substantially cylindrical recess formed radially from the outer circumference of the plate and a suction hole 13 formed through the inner circumferential surface of the cylindrical passage 12 toward the compression chamber outer space (in the circumferential direction). It is.

The cylindrical passage 12 has a coaxial cylindrical surface having three different diameters, and the first cylindrical surface 1a on the open end side of the cylindrical passage 12 becomes the suction pipe connecting portion 12a. The 2nd cylindrical surface 1b and the 3rd cylindrical surface 1c become the check valve sliding part 12b. The 1st cylindrical surface 1a and the 2nd cylindrical surface 1b are comprised in this order, and small internal diameter.

In FIG. 3, the cylindrical passage 12 includes the check valve sliding portion 12b (the second cylindrical surface 1b and the third cylindrical surface 1c) and the cylindrical surface axial direction of the third cylindrical surface 1c. It has the spring seating surface 1d which closes an end surface, and the cylindrical convex part 1e which protrudes toward the check valve 14 provided in the spring seating surface 1d.

(Check Valve Spring)

A suction pipe 3 inserted through the sealed container 10 is connected to the suction pipe connecting portion 12a. Moreover, the check valve 14 and the spring 15 are accommodated in the check valve slide part 12b.

The check valve 14 is guided to the second cylindrical surface 1b and is movable, and has a cup shape for preventing backflow of the refrigerant.

One end of the spring 15 is in contact with the spring seating surface 1d in the suction passage 11, and the other end penetrates from the open end 14c into the check valve (cup) 14 so as to close the inner surface of the closing plate (the bottom of the cup). (B), the check valve 14 is added in the direction which closes the opening of the suction pipe 3. As shown in FIG. And the spring 15 is tapered, and the convex part is made into the small diameter end (henceforth "a seating surface side") 15b of the one where the external shape is small, to the spring seating surface 1d side. It is attached to the outer periphery of (1e).

In the check valve slide portion 12b configured as described above, during the electrostatic operation of the compressor, the check valve 14 presses (compresses) the spring 15 against its applied force, and Open the occlusion. As a result, the suction passage 11 and the suction pipe 3 communicate with each other, the refrigerant is sucked from the suction pipe 3 into the cylindrical passage 12 of the suction passage 11, and passes through the suction hole 13. Is sucked into the compression chamber 1g.

On the other hand, when the compressor is stopped, the check valve 14 closes the opening of the suction pipe 3 by the force of the spring 15 to prevent the backflow of the refrigerant.

(Operation: normal operation)

Next, the operation will be described. When the operation of the scroll compressor 100 starts, the compression chamber 1g becomes a negative pressure to receive the suction refrigerant gas. At this time, this negative pressure acts on the check valve 14 through the suction hole 13 and the cylindrical passage 12, and the check valve 14 is the radius of the scroll compressor 100 against the force of the spring 15. Move to the center of the direction.

As a result, the blockage of the suction pipe 3 is opened, and the suction pipe 3 and the suction passage (cylinder passage 12 and suction hole 13) communicate with each other, and the sealed container 10 is removed from the suction pipe 3. The refrigerant gas is sucked in. The refrigerant gas flows into the outer circumferential portion of the compression chamber 1g (compression chamber outer space 1i) through the suction passage 11 (cylinder passage 12 and suction hole 13). Thereafter, the refrigerant gas is compressed by using the rotational force given through the drive shaft 4 by the electric motor 7, and becomes a high pressure state and is discharged into the closed container 10 from the discharge port 1h formed at the center of the fixed scroll 1. do.

By the high pressure refrigerant gas discharged into the sealed container 10, the inside of the sealed container 10 is filled with a high pressure atmosphere, and the high pressure refrigerant gas passes through the discharge pipe 5 provided in the trunk portion of the sealed container 10. To be discharged out of the sealed container (10).

Lubricant 10a is stored at the bottom of the sealed container 10, and the lower end of the drive shaft 4 is immersed in the lubricant 10a. The oil supply hole 4a is provided in the center of the drive shaft 4, and the bottom part of the sealed container 10 is a compression chamber outer space through this oil supply hole 4a, the oscillation bearing 2a, and the main bearing 6a. Communicating with (1i).

During operation of the scroll compressor 100, since the sealed container 10 is filled with a high pressure atmosphere, the lubricating oil 10a is supplied into the oil supply hole 4a by the differential pressure with the low pressure atmosphere of the suction refrigerant gas. Is raised to lubricate the pivot bearing 2a provided on the swinging scroll 2 and the spindle support 6a provided on the compliant frame 6 before being led to the compression chamber outer space 1i.

(Action: reversing driving)

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, operation of the three-phase induction motor is performed in assembling a unit (for example, an air conditioner). Due to a wiring error of a capacitor or the like, the electric motor 7 may run in reverse in a test of a manufacturing line.

In the case of the brushless DC motor driven by the inverter, since the protection circuit which detects the reverse phase of a power supply and cuts off electricity to a brushless DC motor is normally built in the drive circuit (not shown), 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 cuts off the power supply to the brushless DC motor, the scroll compressor may reverse if there is a connection error in the power supply terminal to the scroll compressor. .

In the connection of a three-phase induction motor, when three power supply terminals (U phase, V phase, W phase) are correctly connected to the glass terminal 16 (refer to FIG. 1) of the scroll compressor, the electric motor 7 generates a predetermined power failure. (正 轉) Perform the operation. However, for example, if the U phase and the V phase are connected incorrectly (the V phase of the power source is connected to the U phase winding and the U phase of the power source is connected to the V phase winding), the electric motor 7 is in a predetermined direction. Rotate in the opposite direction to the electrostatic operation that rotates (reverse operation).

In addition, in the connection of a single phase induction motor, a driving capacitor is usually connected in series with the auxiliary winding, and the series circuit is connected in parallel with the main winding. If the operation capacitor is connected to the main winding due to a connection error of the operation capacitor, and the series circuit is connected to the auxiliary winding in parallel, the motor 7 rotates in the opposite direction to the electrostatic operation rotating in the predetermined direction. Is done.

Next, the reverse operation by the connection error at the time of mounting of the outdoor unit equipped with the scroll compressor 100, and the air conditioner (not shown) provided with an indoor unit is demonstrated. In this case, the scroll compressor 100 which uses a three-phase induction motor for the electric motor 7 is an object.

In the case where the electric motor 7 is a brushless DC motor driven by an inverter, when the reverse circuit of the power supply is detected in the drive circuit and the protection circuit for interrupting the energization to the brushless DC motor is not incorporated, In the connection of the three-phase power supply to the power supply connection terminal, if the order of the phases is out of order, the motor of the scroll compressor performs reverse operation.

Moreover, in the case of the scroll compressor which uses a single phase induction motor for the electric motor 7, even if the order of phases (deviation) shifts in connection of the single phase power supply to the power supply connection terminal of the outdoor unit at the time of mounting, Reversal operation of the electric motor 7 does not occur, but reversal operation due to a wiring error occurs at the time of service (exchange) of the operation capacitor after mounting.

In the above case, when the scroll compressor 100 is inverted, the refrigerant flows backward from the discharge side to the suction side. At this time, the coolant flows from the suction hole 13 toward the cylindrical passage 12 and contacts 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. Since the convex portion 1e is inserted into the spring 15, the spring 15 is provided. The movement of the spring 15 is suppressed, and the spring 15 is prevented from escaping from the suction passage 11. Thereby, the problem that the spring 15 deviates from the suction path 11 in the abnormal mode, such as reverse phase operation, can be eliminated. Therefore, it is possible to resume normal operation by returning to the normal power supply connection state after the reverse phase cancellation, and a highly reliable scroll compressor can be obtained.

However, when the spring 15 has a straight shape, the spring 15 does not deviate so that the spring 15 repeats the expansion and contraction at a high and high speed during the backflow of the refrigerant, so that the spring 15 The outer circumferential surface and the inner circumferential surface of the check valve 14 are rubbed, and the wire rod forming the coil of the spring 15 is shaved or worn, so that the wire rod breaks, that is, the spring 15 is bent. This occurs. Thus, the spring 15 is tapered to prevent such a phenomenon.

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: the outer diameter of the check valve side 15a of the spring 15,

dob: outer diameter of seating surface side 15b of spring 15,

dia: the inner diameter of the check valve side 15a of the spring 15,

dib: inner diameter of seating surface side 15b of spring 15,

Di: inner diameter of the check valve 14,

Do: outer diameter of the convex part 1e,

H: height of the convex portion 1e,

h: cup depth of check valve 14.

In addition, there is a feature in that the relationship between each dimension is a structure that satisfies both Equation 1 and Equation 2.

(Di-doa) <(Di-dob)... ... (Equation 1)

(dib-Do) <(Di-dob)... ... (Equation 2)

In addition, since "h" is the cup depth of the check valve 14, ie, the check valve 14 is in the form of a cup whose one end is blocked by the closing plate 14a (corresponding to the bottom of the cup), the closing plate 14a It corresponds to the distance from the inner surface 14b (corresponding to the inner surface of the bottom of the cup) to the open end 14c (the length in the axial direction of the internal space of the check valve 14).

The height "H" of the convex part 1e is more than the height which one coil takes from the spring 15 in the state which the check valve 14 is closed, and satisfy | fills Formula 3 There is a characteristic in one point.

H <h… ... (Equation 3)

Thus, the scroll compressor 100 makes the shape of the spring 15 into a taper shape, protrudes to the spring seating surface 1d in the suction passage 11 in the expansion-contraction direction of the spring 15, and the spring 15 Since the cylindrical convex part 1e inserted in the inside of () is provided, and also satisfy | fills the dimensional relationship of said Formula 1-Formula 3, since severe detonation of the spring 15 at the time of reverse rotation operation is carried out. Is prevented and the shape of the spring 15 is tapered to satisfy Equations 1 and 2, thereby preventing damage of the spring 15 from rubbing between the inner circumferential surface of the check valve 14 and the outer circumferential surface of the spring 15. It is possible to prevent or to prevent breakage of the seating side of the spring 15 by the check valve 14. In addition, by the taper shape, the inner circumferential surface of the spring 15 does not rub the outer circumferential surface of the cylindrical convex portion 1e, and the breakage of the spring 15 can be prevented, and the expansion and contraction can be made smooth. . That is, even when the check valve 14 is operating during normal operation, the spring 15 needs to counter the force (friction force) rubbed against the inner circumferential surface of the check valve 14 or the outer circumferential surface of the convex portion 1e. Since it can be sufficient to operate only by the force of the spring 15, it can suppress that unnecessary force generate | occur | produces.

In addition, since the inner circumferential surface of the check valve 14 and the outer circumferential surface of the spring 15 are not rubbed, or the inner circumferential surface of the spring 15 and the outer circumferential surface of the cylindrical convex portion 1e are not rubbed, It is possible to secure the service life of springs more than conventionally by using wires by inexpensive materials or processing methods without using expensive wire rods with high durability and complicated and expensive wire processing such as plating and coating. Also, the more reliable one is obtained.

In addition, although the cylindrical convex part 1e is demonstrated with the cylindrical shape of the same outer diameter from the spring seating surface 1d to the tip of the convex part 1e, the outer diameter of the convex part 1e does not necessarily need to be the same. For example, the spring seating surface 1d side may be made into a tapered cylindrical shape having a small diameter. By doing so, the spring 15 is no longer displaced from the convex portion 1e. Moreover, the groove in which the left winding part of the spring 15 is latched in the connection part of a spring seating surface and the convex part 1e may be latched so that the left winding part of the spring 15 may fit. Like the shape of the convex part 1e, the spring 15 becomes hard to escape from the convex part 1e. In addition, the width | variety of the groove | channel at this time is the same as the wire rod wire diameter of the spring 15, and the depth should just be 50% or more of the depth of the wire rod wire diameter of the spring 15. In other words, when the wire rod is inserted into the groove by 50%, the wire rod diameter of the spring 15 is held down by the width of the groove, so that the effect of locking the spring left hand portion is sufficiently obtained.

In addition, the left winding portion of the spring 15 may be in contact with or fixed to the inner surface 14b of the closing plate 14a of the check valve 14, or may be in contact with or fixed to the inner side of the side surface of the check valve 14. none. In other words, the method may be such that the diameter of the left winding portion of the spring 15 is slightly larger than the inner circumference of the check valve 14 so as to be brought into contact with the side surface of the check valve 14 with the force of expanding the left winding portion as the side pressure. Since the spring 15 has a tapered shape, the other part of the spring does not come into contact with the side part of the check valve 14 even when it is stretched. Therefore, the coil of the spring 15 is not rubbed and shaved or worn out. Of course, it may be latched in the form supported by both the side part of the check valve 14, and the inner surface 14b of the blocking plate 14a.

By the above, normal operation can be resumed by returning to normal power supply connection state after reverse operation, and the scroll compressor 100 of high reliability can be obtained.

[Embodiment Mode 2]

FIG. 5 is an enlarged longitudinal sectional view for explaining a configuration of a scroll compressor according to Embodiment 2 of the present invention, in the vicinity of a suction passage. In addition, each figure is shown typically, and is not limited to the shape of each structural member, or the form of illustration. In addition, the same code | symbol is attached | subjected to the part same or equivalent part as Embodiment 1, and the description of a part is abbreviate | omitted.

In FIG. 5, the scroll compressor 200 has a spring 17 having a shape in which two cylindrical springs whose outer diameters are easier to process than the tapered spring 15 of the scroll compressor 100 are combined. Have

That is, the spring 17 is seated in a water winding whose outer diameter is smaller than the inner diameter of the check valve side cylindrical spring portion (large diameter portion) 17a of the water winding and the check valve side cylindrical spring portion 17a. It is formed by the surface side cylindrical spring part (small diameter part) 17b. Therefore, similarly to the spring 15, it is possible to prevent the seating surface side 17b of the spring 17 from being crushed by the check valve 14, or rubbing the inner circumferential surface of the check valve 14 and the outer circumferential surface of the spring 17.

The shape of the spring 17 is the shape which combined the check valve side cylindrical spring part 17a and the seating surface side cylindrical spring part 17b, The code | symbol which shows the dimension means the following.

doa: Outer diameter of the check valve 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: the inner diameter of the check valve side cylindrical spring portion 17a,

dib: the inner diameter of the seating surface side cylindrical spring portion 17b,

Di: inner diameter of the check valve 14,

Do: outer diameter of the convex part 1e,

La: length of the check valve side cylindrical spring portion 17a of the spring 17 in the state where the check valve 14 is closed,

Lb is the length of the seating surface side cylindrical spring portion 17b with the check valve 14 closed,

H: height of the convex portion 1e,

h: Distance between the inner surface 14b of the blocking plate 14a of the check valve 14, and the open end 14c of the check valve 14 (the length in the axial direction of the internal space of the check valve 14).

And each dimension has the relationship of Formula 4-Formula 6.

(Di-doa) <(Di-dob)... ... (Equation 4)

(dib-Do) <(Di-dob)... ... (Eq. 5)

La? ... (Equation 6)

In addition, the height H of the convex part 1e is more than the height which one winding of the seating surface side cylindrical spring part 17b of the spring 17 takes, and the dimension of Formula H <h in the state which the check valve 14 closed. It is characterized by a structure that satisfies the relationship.

H <h… ... (Equation 7)

Thereby, an effect equivalent to the tapered shape can be acquired by the spring which can be made by cheap design processing.

By the above, normal operation can be resumed by returning to normal power supply connection after reverse operation, and a highly reliable scroll compressor can be obtained.

[Embodiment 3]

FIG. 6 is an enlarged longitudinal sectional view for explaining a configuration of a scroll compressor according to a third embodiment of the present invention (near the suction passage). FIG. In addition, each figure is shown typically, and is not limited to the shape of each structural member, or the form of illustration. In addition, the same code | symbol is attached | subjected to the part same or equivalent part as Embodiment 1, and the description of a part is abbreviate | 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", and is smaller than the depth h of the cup of the check valve 14 (the distance from the inner surface 14b of the blocking plate 14a to the open end 14c). That is, Expression 8 is satisfied.

Hs <h… ... (Expression 8)

Here, the contact height Hs is the height of the whole spring 18 in the state in which the spring 18 is depressed and contracted and the coils contact. When the spring 18 is pressed up to the contact height Hs, excessive stress is generated in the spring 18.

In Fig. 6, when the check valve 14 is pressurized as far as possible against the biasing force of the spring 15, since the open end 14c of the check valve 14 abuts the spring seating surface 1d, the spring 18 ) Is the depth "h" of the cup of the check valve 14. That is, when the spring 18 is most compressed, it will contract to this length "h".

Therefore, for example, when the length h in the spring receiving space is shorter than the contact height Hs of the spring 18, excessive stress occurs in the spring 18, and if such pressurization is repeated for a long time, the spring 18 may be broken. However, since the scroll compressor 300 has a form that satisfies Equation 8, the spring 18 does not contract to the contact height Hs, and contact (pressing) of the wires of the coils is prevented. That is, the wire rods of the coils can be prevented from being hurt each other.

In addition, since the wires of the coils are not injured with each other, it is inexpensive to protect the surface of the wires without using expensive wire rods with high durability or complicated and expensive surface processing such as plating and coating. With the coil using the wire material by the material and the processing method, the lifetime of the spring more than before can be ensured, and the thing more reliable also with respect to a long time use is obtained.

Next, the operation by the structure of the feature portion of the scroll compressor 300 will be described. 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 in the suction passage 11, and the check valve 14 is pressed in a direction against the force of the spring 18. At this time, even if the check valve 14 is pressurized 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 is not contracted to the contact height Hs.

As described above, in the scroll compressor 300, the closing valve 14 of the spring seating surface 1d and the check valve 14 in the state where the check valve 14 is pushed as far as possible in the direction against the force of the spring 18. By constructing the distance h between the 14a larger than the contact height Hs of the spring 18, the excessive stress is not generated in the spring 18 and the spring 18 is contracted to the contact height. The wire rods of the coils are not more in contact with each other and pressurized to damage or damage the wire rods, and are more reliable than Embodiments 1 and 2, which can prevent damage to the spring 18 in long-term use. The scroll compressor 100 can be obtained.

[Fourth Embodiment]

7 to 9 illustrate the structure of the scroll compressor according to the fourth embodiment of the present invention, in which FIG. 7 is a front view showing a part (spring) by drawing, 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 as much as possible. In addition, each figure is shown typically, and is not limited to the shape of each structural member, or the form of illustration. In addition, the same code | symbol is attached | subjected to the part same or equivalent part as Embodiment 1, and the description of a part is abbreviate | omitted.

In FIG. 7, the scroll compressor 400 has a spring 19 in place of the spring 15 of the scroll compressor 100.

As for the spring 19, the end of turn of the check valve side 19a is bent to the inner side (center axis side), and a straight bent portion 19c is formed to be continuous at the end of the winding.

Therefore, when the spring 19 is provided 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, when the spring 19 is to be installed in the wrong posture shown in Fig. 8B, the bent portion 19c formed on the check valve side 19a of the spring 19 is the top of the convex portion 1e. The spring 19 cannot be installed in the convex portion 1e because it rises up (butts).

Therefore, according to the spring 19, the problem of installing upside down is eliminated.

In addition, as shown in FIG. 9, when the outer diameter (the same as the outer diameter of the bent part 19c) of the wire rod which forms the spring 19 is set to "e",

e <(h-H)... ... (Equation 9)

.

Therefore, even when the check valve 14 is press-fitted to the maximum (the state where the open end 14c of the check valve 14 abuts against the spring seating surface 1d), the bent portion 19c of the spring 19 is convex. It is pinched by the part 1e and the check valve 14, and is not broken.

In addition, although the bending part is provided about the spring 15 in Embodiment 1, this invention is not limited to this, It is bending in the spring 17, 18 in Embodiment 2, 3 You may form a part.

As a result, a scroll compressor with fewer assembly errors can be configured even when the compressor is assembled, and a highly reliable scroll can be obtained even during operation in which the spring is not damaged even when the check valve is fully pushed in. A 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 chamber outer space 2: swinging scroll
2a: swing shaft bearing 3: suction pipe
4 driving shaft 4a oil supply hole
5: exhaust pipe 6: compliant frame
6a: spindle support 7: electric motor
10: sealed container 10a: lubricating oil
11: suction passage 12: cylindrical passage
12a: suction pipe connection 12b: check valve sliding portion
13 suction hole 14 check valve
14a: occlusion board 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 part 17b: seating surface side cylindrical spring part
18: Spring (Embodiment 3) 19: Spring (Embodiment 4)
19a: check valve side 19b: half check valve side
19c: bend 50: frame
60: compressor mechanism
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: Inner diameter of check valve side cylindrical spring
dib: Inner diameter of seating surface side cylindrical spring
doa: Outer diameter of check valve side cylindrical spring
dob: Outer diameter of seat spring
e: spring diameter
h: axial length of the internal space of the check valve
H: convex height
Hs: tight height.

Claims (4)

Airtight containers,
Fixed scrolls and swinging scrolls provided in the sealed container and engaged with each other such that compression chambers are formed by respective spiral teeth;
A drive shaft for driving the rocking scroll and an electric motor for driving the drive shaft;
A frame constituting a compressor mechanism together with the fixed scroll and the swinging scroll;
A suction pipe inserted through the sealed container;
A suction passage provided near the outer circumference of the fixed scroll, the suction pipe being connected at the outer circumferential end in the radial direction,
A check valve disposed freely in the suction passage and capable of closing the opening of the suction pipe;
A spring installed in the suction passage, for biasing the check valve in the direction of the suction pipe,
On the circumferential side surface of the suction passage, a suction port communicating with the compression chamber, a spring seating surface where one end portion of the spring abuts against a radially inner peripheral end of the suction passage, and the checker is placed on the spring seating surface. A convex portion protruding toward the valve and penetrating into the spring,
The outer diameter of the end part which abuts the said spring seating surface of the said spring is smaller than the outer diameter of the end part which abuts the said check valve of the said spring,
The check valve is a bottomed cylinder whose one end is opened and the other end is closed by a occlusion plate,
One end of the spring is in contact with the spring seating surface, and the other end of the spring is in contact with the inner surface of the closure plate by entering from the opened end in the check valve,
The distance between the open end and the inner surface of the closure plate is greater than the contact height of the spring,
And a bending portion bent inward in the radial direction at an end portion in contact with the inner surface of the closure plate of the spring. The method of claim 1,
The outer diameter of the spring varies smoothly or stepwise from one end to the other end. delete delete

Images