CN202510366U - Scroll compressor - Google Patents

Abstract

The utility model discloses a scroll compressor. The scroll compressor (1) includes: a flange part receiving part (54) and a through hole (53) that is recessed on the end surface of one side of the compression mechanism (10) and accommodates the flange part (33) of the orbiting scroll (30). . The through hole (53) extends from the bottom surface of the flange part housing part (54), and the drive shaft (80) is inserted into and supported by the through hole (53). On the end surface of the compression mechanism (10) side of the fixed member (50), a sealing ring groove formed in an annular shape outside the opening of the flange part housing part (54) and supporting the sealing ring (58) is provided. (57). An annular slit (59) is formed on the outside of the through hole (53) on the bottom surface of the flange portion receiving portion (54), and the outer diameter d1 of the slit (59) and the flange portion receiving portion (54) are in the compression mechanism ( 10) The opening diameter d2 on one side satisfies the relationship that d1 is greater than or equal to d2.

Description

scroll compressor

technical field

The utility model relates to a scroll compressor with a static scroll and a movable scroll, in particular to a scroll compressor which reduces the thrust loss of each scroll. the

Background technique

Heretofore, scroll compressors in which a fixed scroll and an orbiting scroll mesh to form a compression chamber have been known. For example, Patent Document 1 discloses such a scroll compressor. In this scroll compressor, the movable scroll connected to the tip of the drive shaft rotates eccentrically to suck fluid into the compression chamber, compress it, and then discharge it to the outside after becoming high-pressure fluid. In addition, in the above-mentioned scroll compressor, in order to make the movable scroll move away from the fixed scroll without being affected by the pressure in the compression chamber, it is brought by the back pressure space provided on the back side of the movable scroll. The pressure pushes the movable scroll to the side of the static scroll. The back pressure space is divided into an inner peripheral side and an outer peripheral side by a seal ring. The first back-pressure space on the inner side is given a high pressure, and the second back-pressure space on the outer side is given a lower pressure than the first back-pressure space. The scroll compressor performs back pressure control by adjusting the pressure of the two back pressure spaces. the

On the other hand, since the movable scroll rotates eccentrically in the scroll compressor, the drive shaft connected to the movable scroll tends to incline. If the drive shaft is inclined, the drive shaft will be in a point contact state at the bearing portion, and wear will occur on the drive shaft and the bearing portion. Then, in the scroll compressor of Patent Document 1, an annular slit is provided in the bearing portion, and the drive shaft is allowed to incline by elastic bending of the inner wall portion of the slit. the

Patent Document 1: Japanese Laid-Open Patent Gazette, Japanese Patent Application Laid-Open No. 2003-97458

Utility model content

－Technical problems to be solved by the utility model－

However, in conventional scroll compressor configurations, the seal ring is arranged on the outer peripheral side of the gap. In this way, when the sealing ring is arranged on the outer peripheral side, the high-pressure first back pressure space is relatively increased, which increases the thrust on the orbiting scroll brought by the back pressure space. As a result, the orbiting scroll and the fixed scroll are closely attached to each other, and frictional loss, which is called excess thrust, reduces the durability of the scroll compressor, which becomes a problem. the

The utility model is completed in view of the above points, and its purpose is to suppress the increase of the thrust loss caused by the excess thrust force of the movable scroll by relatively reducing the first back pressure space. the

－Technical solutions to solve technical problems－

The scroll compressor of the utility model according to the first aspect includes: a fluid compression mechanism 10 having a fixed scroll 20 and a movable scroll 30 ; 80 and a fixed member 50 disposed on the rear side of the movable scroll 30 and forming a back pressure space 100 between the movable scroll 30 . On the fixing member 50, a flange portion receiving portion 54 and a through hole 53 are formed. The direction is circular and accommodates the flange portion 33 of the movable scroll 30. The through hole 53 extends from the bottom surface of the flange portion receiving portion 54. The drive shaft 80 is inserted into the through hole 53 and passed through the through hole 53. Hole 53 supports. A seal ring groove 57 is provided on the end surface of the fixed member 50 on the side of the compression mechanism 10, and the seal ring groove 57 is formed in a ring shape outside the opening of the flange part housing part 54, and is opposed to the moving part. The back surface of the scroll 30 is in close contact with the back pressure space 100 and is supported by the seal ring 58 that divides the inner peripheral side and the outer peripheral side. An annular slit 59 is formed outside the through hole 53 on the bottom surface of the flange housing portion 54 of the fixing member 50 . The outer diameter d1 of the slit 59 and the opening diameter d2 of the flange receiving portion 54 on the side of the compression mechanism 10 satisfy the relationship that d1 is greater than or equal to d2. the

In the present invention, the opening of the flange portion receiving portion 54 on the side of the compression mechanism 10 is formed such that its opening diameter is equal to or smaller than the outer diameter of the slit 59 . When the opening is formed smaller, the diameter of the seal ring 58 supported by the seal ring groove 57 formed outside the opening can be reduced. And, by reducing the diameter of the seal ring 58, the area where the high pressure in the back pressure space on the inner peripheral side of the seal ring 58 acts on the movable scroll 30 is relatively reduced, so that the pushing force on the movable scroll 30 can be reduced. pressure. Therefore, it is possible to set the pressing force at a lower value than in the prior art, and it is possible to increase the degree of freedom in designing the pressing force. As a result, an increase in thrust loss due to excess pressing force can be suppressed. the

In the utility model of claim 2, in the utility model of claim 1, the opening of the compression mechanism 10 side of the flange part housing part 54 is configured so that the ring member 71 is fitted therein. the

In the present invention, the ring member 71 is provided on the flange portion housing portion 54 . The ring member 71 is fitted in, and the ring member 71 forms an opening of the flange portion housing portion 54 on the side of the compression mechanism 10 . For this reason, the opening can be reduced by the ring member 71 , so that the diameter of the seal ring 58 supported by the seal ring groove 57 formed outside the opening can be reduced. the

In the utility model of the third aspect, in the utility model of the second aspect, the seal ring groove 57 is formed by cutting the outer peripheral corner of the upper surface of the ring member 71 around the entire circumferential direction. the

In the invention of this aspect, the upper surface of the ring member 71 is provided with a notch portion formed by cutting the outer peripheral corner around the entire circumferential direction. When the ring member 71 is embedded, a seal ring groove 57 is formed by the notch and the inner peripheral surface of the embedded portion of the ring member 71 . For this reason, a seal ring groove 57 can be formed close to the opening of the flange portion housing portion 54 on the compression mechanism 10 side, and the diameter of the seal ring 58 supported by the seal ring groove 57 can be reduced. the

In the utility model of the fourth aspect, in the utility model of the second aspect, the seal ring groove 57 is constituted by a groove portion formed by cutting the upper surface of the ring member 71 around the entire circumferential direction. the

In the present invention, the upper surface of the ring member 71 is provided with a groove portion formed around the entire circumferential direction, and the seal ring groove 57 is formed by this groove portion. For this reason, a seal ring groove 57 can be formed close to the opening of the flange portion housing portion 54 on the compression mechanism 10 side, and the diameter of the seal ring 58 supported by the seal ring groove 57 can be reduced. the

In the utility model of the fifth aspect, in the utility model of the second aspect, the sealing ring groove 57 cuts the upper surface of the part where the ring member 71 is embedded in the flange part receiving part 54 around the entire circumferential direction. The cutout formed by the inner peripheral corner of the the

In the present invention, a notch formed by cutting an inner peripheral corner around the entire circumferential direction is provided on the upper surface of the portion where the ring member 71 is fitted in the flange portion housing portion 54 . When the ring member 71 is embedded, a seal ring groove 57 is formed by the notch and the outer peripheral surface of the ring member 71 . For this reason, a seal ring groove 57 can be formed close to the opening of the flange portion housing portion 54 on the compression mechanism 10 side, and the diameter of the seal ring 58 supported by the seal ring groove 57 can be reduced. the

According to the utility model of the sixth aspect, in the utility model of the second aspect, the sealing ring groove 57 is embedded in the upper surface of the ring member 71 and the flange portion receiving portion 54 by straddling the entire circumferential direction. The groove portion formed on the upper surface of the portion of the ring member 71 is constituted. the

In the present invention, grooves are provided on the upper surfaces of the ring member 71 and the flange housing portion 54 where the ring member 71 is fitted. The groove portion is formed around the entire circumferential direction across the ring member 71 and the portion, and the seal ring groove 57 is formed by this groove portion. For this reason, a seal ring groove 57 can be formed close to the opening of the flange portion housing portion 54 on the compression mechanism 10 side, and the diameter of the seal ring 58 supported by the seal ring groove 57 can be reduced. the

According to the utility model of the seventh aspect, in the utility model of the first aspect, the through hole 53 is configured to have a cylindrical member 76 embedded therein, and at least the inner peripheral wall of the gap 59 is formed by the cylindrical member 76 . the

In the present invention, the cylindrical member 76 is embedded to form the through hole 53 . In addition, at least the inner peripheral wall of the slit 59 is constituted by the cylindrical member 76 . That is, the slit 59 is formed by a different member, that is, the cylindrical member 76. Therefore, there is no need to cut grooves in the integrally formed fixing member 50 to form the slit 59 , and it is not necessary to enlarge the opening of the flange accommodating portion 54 to prevent collision of cutting tools. Thus, in the scroll compressor 1, the seal ring groove 57 can be formed close to the opening of the flange portion housing portion 54 on the side of the compression mechanism 10, and the diameter of the seal ring 58 supported by the seal ring groove 57 can be adjusted. decrease. the

In the eighth invention, in the seventh invention, the slit 59 is formed by a notch formed by cutting the outer peripheral side of the cylindrical member 76 around the entire circumferential direction. the

In the present invention, the cylindrical member 76 is provided with a notch formed by cutting the outer peripheral side around the entire circumferential direction. The slit 59 is formed by the notch and the inner peripheral surface of the portion where the cylindrical member 76 is fitted. the

In the utility model of claim 9, in the utility model of claim 7, the slit 59 is formed by cutting the inner peripheral side of the part where the cylindrical member 76 is embedded around the entire circumferential direction. the

In the present invention, a cutout portion formed by cutting the inner peripheral side around the entire circumferential direction is provided at a portion where the cylindrical member 76 is fitted. The slit 59 is formed by the notch and the outer peripheral surface of the cylindrical member 76 . the

－Effects of utility model－

According to the scroll compressor of the present invention, the outer diameter d1 of the gap 59 and the opening diameter d2 of the flange receiving portion 54 on the side of the compression mechanism 10 satisfy the relationship that d1 is greater than or equal to d2. As a result, the flange housing portion 54 has a smaller opening on the side of the compression mechanism 10 than in the prior art, so the diameter of the seal ring 58 supported by the seal ring groove 57 formed outside the opening is also smaller than in the prior art. In this way, when the diameter of the sealing ring 58 becomes smaller, the area where the high pressure of the back pressure space on the inner peripheral side of the sealing ring 58 acts on the movable scroll 30 is relatively reduced, so that the pushing force on the movable scroll 30 can be reduced. pressure. For this reason, the pushing force can be set lower than in the prior art, so that the degree of freedom in designing the pushing force can be increased. As a result, an increase in thrust loss due to excess pressing force can be suppressed. the

According to the second aspect of the invention, the ring member 71 opening on the side of the compression mechanism 10 constituting the flange portion accommodating portion 54 is fitted inside. Assuming that the fixing member 50 is integrally formed, when forming the slit 59 by cutting, the cutting tool is affected by the size of the opening of the flange housing portion 54, and the processing is difficult. However, in the utility model of this aspect, by embedding another member, that is, the ring member 71, and cutting the gap 59 in a state before the ring member 71 is embedded, the cutting tool is no longer affected by the size of the opening. The slit 59 can be easily formed. Furthermore, by inserting the ring member 71 after the slit 59 is formed, it is possible to easily form the fixing member 50 which has been difficult to process until now. Also, since the processing becomes easier, the shape accuracy of the fixing member 50 is improved, and the rotation of the scroll compressor 1 is more stable. the

According to the seventh aspect of the invention, the cylindrical member 76 constituting the through hole 53 is embedded, and at least the slit 59 of the cylindrical member 76 constitutes the inner peripheral wall. That is, the slit 59 is formed by a different member, that is, the cylindrical member 76 . Therefore, it is no longer necessary to directly cut the slit on the fixing member 50, and it is no longer necessary to enlarge the opening of the flange portion housing portion 54 so as not to affect the cutting tool. Accordingly, the opening of the flange housing portion 54 on the compression mechanism 10 side can be reduced, and the diameter of the seal ring 58 supported by the seal ring groove 57 formed outside the opening can be reduced. In addition, the area where the high pressure in the back pressure space on the inner peripheral side of the seal ring 58 acts on the movable scroll 30 is relatively reduced, thereby suppressing an increase in thrust loss. the

Description of drawings

Fig. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention. the

Fig. 2 is a longitudinal sectional view showing a part of the scroll compressor according to the first embodiment of the present invention. the

3 is a longitudinal sectional view showing a part of the scroll compressor according to Modification 1 of the first embodiment of the present invention. the

4 is a longitudinal sectional view showing a part of a scroll compressor according to Modification 2 of the first embodiment of the present invention. the

5 is a longitudinal sectional view showing a part of a scroll compressor according to a second embodiment of the present invention. the

6 is a longitudinal sectional view showing a part of a scroll compressor according to a third embodiment of the present invention. the

7 is a longitudinal sectional view showing a part of a scroll compressor according to a fourth embodiment of the present invention. the

8 is a longitudinal sectional view showing a part of a scroll compressor according to a fifth embodiment of the present invention. the

9 is a longitudinal sectional view showing a part of a scroll compressor according to a sixth embodiment of the present invention. the

-Symbol Description-

1-scroll compressor; 10-compression mechanism; 20-static scroll; 30-moving scroll; 33-flange; 50-shell; 53-through hole; 54-flange storage part; 56-shaft 57-seal ring groove; 58-seal ring; 59-gap; 71-ring component; 76-cylindrical component; 80-drive shaft; 100-back pressure space. the

Detailed ways

Hereinafter, embodiment of this invention is described in detail based on drawing. In addition, the following embodiments and modified examples are merely preferable examples in nature, and are not intended to limit the present invention and its application or its range of applications. the

(first embodiment)

The first embodiment of the present invention will be described. The scroll compressor 1 of the first embodiment shown in FIGS. 1 and 2 is a compressor that is connected to a refrigerant circuit (not shown) that circulates a refrigerant to perform a refrigeration cycle, and compresses a refrigerant. the

The scroll compressor 1 includes a compression mechanism 10 , a driving motor 40 , a housing 50 , and a casing 90 . the

Said housing 90 is composed of a cylindrical trunk with an axis in the up-down direction, i.e. a housing body 91, a bowl-shaped upper wall 92 welded to the upper end of the housing body 91 and having an upwardly protruding convex surface in an airtight manner, and an airtight ground. It is welded to the lower end of the housing body 91 and has a bowl-shaped bottom wall 93 protruding downward. A suction pipe 94 leading the refrigerant of the refrigerant circuit to the compression mechanism 10 penetrates and is fixed to the upper wall portion 92 . In addition, a discharge pipe 95 for spraying the refrigerant in the casing 90 to the refrigerant circuit penetrates and is fixed to the casing body 91 . An oil storage portion 96 for storing lubricating oil is formed on the bottom wall portion 93 of the casing 90 . the

The compression mechanism 10 and the drive motor 40 disposed below the compression mechanism 10 are accommodated inside the casing 90 . Further, a drive shaft 80 that transmits the rotational driving force of the drive motor 40 to the compression mechanism 10 is connected to the compression mechanism 10 and the drive motor 40 . the

The drive shaft 80 has a main shaft part 81 extending in the vertical direction inside the casing 90, an eccentric part 82 protruding from the upper end surface of the main shaft part 81 and connected to the compression mechanism 10, and an approximate shaft formed on the main shaft part 81. The central part is a balance weight part 83 for obtaining dynamic balance during rotation. Also, an oil supply passage 84 penetrating from the upper end to the lower end of the drive shaft 80 is provided inside the drive shaft 80 . The lower end of the drive shaft 80 is immersed in the oil reservoir 96 . the

The drive motor 40 is composed of a stator 41 and a rotor 42 . The stator 41 is fixed on the inner surface of the casing body 91 by shrink fitting or other methods. The rotor 42 is arranged inside the stator 41 and is provided coaxially with the main shaft portion 81 of the drive shaft 80 so as to be non-rotatable. the

The fixing member 50 is airtightly pressed and fixed on the casing body 91 , and the inside of the casing 90 is divided into an upper space 97 for accommodating the compression mechanism 10 and a lower space 98 for accommodating the drive motor 40 . the

The compression mechanism 10 is arranged on the fixed part 50 , including a fixed scroll 20 fixed on the upper surface of the fixed part 50 and arranged between the fixed scroll 20 and the fixed part 50 and engaged with the fixed scroll 20 The moving scroll 30. the

The fixed scroll 20 has an end plate 21, a scroll-shaped (involute) lap (lap) 22 formed on the front surface of the end plate 21 (the lower surface in FIGS. 1 and 2 ), and a lap located on the lap. The outer peripheral wall portion 23 formed continuously with the spiral tooth 22 on the outer peripheral side of the tooth 22. The lower end surface of the spiral tooth 22 and the lower end surface of the outer peripheral wall portion 23 are formed so as to be substantially on the same plane. In addition, the fixed scroll 20 is fixed to the upper surface of the fixed member 50 by the outer peripheral wall portion 23 . the

On the other hand, the movable scroll 30 includes an end plate 31 and a spiral (involute) wrap 32 formed on the front surface (the upper surface in FIGS. 1 and 2 ) of the end plate 31 . The movable scroll 30 is configured such that the spiral teeth 32 of the movable scroll 30 mesh with the spiral teeth 22 of the fixed scroll 20 . In addition, a space is partitioned between the fixed scroll 20 and the movable scroll 30 by the two wraps 22 , 32 , and the compression chamber 11 is formed by this space. the

In addition, a flange portion 33 is integrally formed on the center portion of the back surface of the end plate 31 of the movable scroll 30 . A bearing 34 is press-fitted into the flange portion 33 , and the eccentric portion 82 of the drive shaft 80 is inserted into the bearing 34 . the

Further, a high-pressure oil introduction passage 35 for supplying lubricating oil to the sliding surface of the movable scroll 30 from the oil supply passage 84 of the drive shaft is provided inside the end plate 31 of the movable scroll 30 . The high-pressure oil introduction passage 35 is formed such that the inside of the flange portion 33 where the upper end of the oil supply passage 84 is opened communicates with the front surface side of the end plate 31 of the movable scroll 30 . Furthermore, in the high-pressure oil introduction passage 35, a flow restricting member 36 having a spiral passage on the outer periphery and controlling the supply amount of oil is inserted. the

A suction port 24 is provided on the outer peripheral wall portion 23 of the fixed scroll 20 , and the suction pipe 94 is airtightly joined to the suction port 24 . the

In addition, the static scroll 20 includes a high-pressure portion 25 recessed at the center of the back surface of the end plate 21 and a discharge port 26 penetrating from the center of the bottom surface of the high-pressure portion 25 to the front surface of the end plate 21 . On the bottom surface of the high-pressure portion 25, a reed valve 27 is provided as a check valve that blocks a passage communicating with the compression chamber. That is, when the pressure of the compression chamber 11 exceeds a predetermined pressure, the reed valve 27 opens, and the compression chamber 11 communicates with the high-pressure portion 25 . In addition, the high-pressure portion 25 is closed by a cover 28 . The high-pressure part 25 and the upper space 97 are partitioned by the cover 28 . the

In addition, in order to make the high-pressure portion 25 communicate with the lower space 98, a first flow path (not shown) that is open to the high-pressure portion 25 is formed on the fixed scroll 20 , and on the fixed member 50 A second flow path (not shown) communicating with the first flow path (not shown) and the lower space 98 is formed. the

The fixing member 50 includes a casing body 51 into which the drive shaft 80 is inserted, and is pressed and fixed on the casing body 91 in an airtight manner. The fixed scroll 20 is fixed on the outer peripheral side of the upper surface of the housing body 51 . In addition, the casing body 51 is formed with a cylindrical concave portion 52 in the center of the upper surface and a through hole 53 leading from the bottom surface of the concave portion 52 to the lower end. the

An annular ring member 71 is provided in the opening of the concave portion 52 . The ring part 71 is embedded in the recess 52, so that the upper surface of the housing body 51 and the upper surface of the ring part 71 are substantially on the same plane, and its downward movement is restricted by a stopper (stopper) 72. Also, in order to limit the downward movement of the ring member 71, the method of pressing the ring member 71 into the recess 52 can be adopted instead of the stopper 72, or the dual measures of pressing and the stopper 72 can be taken at the same time. the

The flange portion 33 is housed in a convex-shaped space in longitudinal cross-section formed by fitting the ring member 71 into the concave portion 52 . That is, the flange portion accommodating portion 54 of the fixing member 50 is constituted by the ring member 71 and the concave portion 52 . The opening of the flange housing 54 on the side of the compression mechanism 10 is formed by the opening of the ring member 71 . the

A bearing 55 is pressed into the through hole 53 of the fixing member 50 , and the upper end of the main shaft portion 81 is rotatably supported by the bearing 55 . That is, a shaft support portion 56 in which the drive shaft 80 is inserted into the through hole 53 and the bearing 55 and supported by the through hole 53 and the bearing 55 is formed on the fixing member 50 . the

An outer peripheral corner portion of the upper surface of the ring member 71 is cut around the entire circumferential direction, and an annular seal ring groove 57 is formed by the formed cut portion and the inner wall of the concave portion 52 . In addition, the notch may be formed by cutting at least an outer peripheral corner of the upper surface of the ring member 71 . In addition to the stepped shape shown in FIG. 2 , the shape of the notch may be various shapes formed by cutting the corners of the outer periphery. the

A seal ring 58 is fitted into the seal ring groove 57 , and the seal ring 58 is supported so as to be in contact with the back side of the end plate 31 of the movable scroll 30 . That is, the sealing ring 58 divides the back pressure space 100 formed between the fixed member 50 and the movable scroll 30 into a first back pressure space 101 on the inner peripheral side of the sealing ring 58 and a second back pressure space 101 on the outer peripheral side of the sealing ring 58 . Pressure space 102 . the

The back pressure space 100 is formed between the end plate 31 of the movable scroll 30 and the fixed member 50 , and is a space where back pressure for pushing the movable scroll 30 toward the fixed scroll 20 acts. the

The first back pressure space 101 is mainly a space formed by the flange portion housing portion 54 . The second back pressure space 102 is formed by the gap between the upper surface of the casing body 51 and the back surface of the movable scroll 30 . In addition, the second back pressure space 102 communicates with the upper space 97 in the housing 90 through a concave portion (not shown) provided on the outer peripheral side of the upper surface of the housing body 51 . the

In addition, the Oldham coupling 105 is provided in the second back pressure space 102, the keyway (not shown) formed on the back of the end plate 31 of the movable scroll 30 and the keyway (not shown) formed on the upper surface of the housing body 51 ) to form the Oldham coupling, which is used to prevent the movable scroll 30 from rotating. the

In addition, an annular gap 59 is formed outside the through hole 53 on the bottom surface of the concave portion 52 . The slit 59 allows the drive shaft 80 to tilt due to the elastic bending of the inner wall of the slit 59 , and prevents the drive shaft 80 from point contact. the

The fixing member 50 of the present embodiment is formed such that the outer diameter d1 of the slit 59 and the opening diameter d2 of the flange receiving portion 54 on the side of the compression mechanism 10 satisfy the relationship that d1 is greater than or equal to d2. Specifically, the inner diameter d2 of the ring member 71 forming the opening of the flange portion housing portion 54 on the compression mechanism 10 side is formed to be equal to or smaller than the outer diameter d1 of the slit 59 . the

－Operating action－

When the driving motor 40 is operated, the movable scroll 30 of the compression mechanism 10 is driven to rotate. The movable scroll 30 revolves around the axis of the main shaft portion 81 while being prevented from rotating by the Oldham coupling 105 . As the movable scroll 30 orbits, the volume of the compression chamber 11 contracts toward the center, and the refrigerant gas sucked in from the suction pipe 94 in the compression chamber 11 is compressed. The compressed refrigerant gas is discharged to the high pressure part 25 through the discharge port 26 of the fixed scroll 20 . The high-pressure refrigerant gas that has been sprayed to the high-pressure part 25 flows to the lower space 98 of the casing 90 through the first flow passage of the fixed scroll 20 and the second flow passage of the fixed member 50, and then sprays to the outside of the casing 90 from the discharge pipe 95. out. the

The lower space 98 of the casing 90 has the same pressure as the ejected high-pressure refrigerant gas, that is, the ejection pressure, and the ejection pressure also acts on the oil in the oil storage portion 96 below the lower space 98 . As a result, the oil in the oil storage portion 96 flows from the lower end of the oil supply passage 84 of the drive shaft 80 to the upper end, and flows out into the flange portion 33 of the movable scroll 30 . The oil supplied to the flange portion 33 lubricates the sliding surfaces of the bearing 34 of the flange portion 33 and the eccentric portion 82 of the drive shaft 80 , and then flows out into the flange portion housing portion 54 (namely, the first back pressure space 101 ). . In this way, the first back pressure space 101 is filled with high-pressure oil, and its pressure is equal to the discharge pressure. In addition, the high-pressure oil in the supply flange portion 33 enters the high-pressure oil introduction passage 35, and the supply amount is controlled by the flow rate limiting member 36, and is supplied to the sliding surfaces of the movable scroll 30 and the fixed scroll 20, and the sliding surfaces are lubricated. the

On the other hand, the upper space 97 separated from the high-pressure portion 25 by the cover 28 is at a lower pressure than the high-pressure portion 25 . For this reason, the pressure of the second back pressure space 102 communicating with the upper space 97 is also low pressure. However, unlike the present embodiment, when a communication path (not shown) is provided in the middle of the compression path from the outer periphery to the discharge port 26, the upper space 97 and the second back pressure space 102 have a pressure in the middle of compression (intermediate pressure). . In this case, for example, a communication path is provided in the fixed scroll 20 so that the compression chamber 11 in the middle of compression communicates with the upper space 97 . The refrigerant gas in the compression chamber 11 is gradually compressed to a predetermined intermediate pressure, and the reed valve (not shown) installed at the end of the communication path is opened, and a part of the refrigerant gas passes through the communication path to the upper space 97 and the second The back pressure space 102 flows out. In this way, the upper space 97 and the second back pressure space 102 have a pressure between the high pressure and the low pressure (intermediate pressure). the

In this way, the first back pressure of the first back pressure space 101 which becomes the discharge pressure and the second back pressure of the second back pressure space 102 which becomes the low pressure (or intermediate pressure) act on the pressure of the end plate 31 of the movable scroll 30. On the back side, the movable scroll 30 is pushed toward the fixed scroll 20 side by the two back pressures. The pushing force is a separation force that acts on the movable scroll 30 to separate the movable scroll 30 from the fixed scroll 20 when the refrigerant gas is compressed, that is, it resists the desire to pull the movable scroll 30 from the fixed scroll 20. The power to open. The separation force is reduced by this pushing force, and the inclination (tipping) of the movable scroll 30 due to the separation force is prevented. the

Under certain design conditions such as the size of the compressor and the compression ratio, there will be an excess of pushing force. If the pressing force becomes excessive, the close contact between the fixed scroll 20 and the movable scroll 30 will increase, and the friction loss, that is, the so-called thrust loss will increase. As a result, the durability of the scroll compressor decreases. the

Therefore, in the present embodiment, the fixing member 50 is formed such that the outer diameter d1 of the slit 59 and the opening diameter d2 of the flange housing portion 54 on the compression mechanism 10 side satisfy the relationship that d1 is greater than or equal to d2. Specifically, since the ring member 71 is fitted into the concave portion 52 of the housing body 51, the opening of the flange portion accommodating portion 54 is formed smaller than in the prior art. Furthermore, the seal ring groove 57 is formed by a cutout portion located near the opening of the flange portion housing portion 54 . Therefore, the separation position of the seal ring 58 from the back pressure space 100 can be provided closer to the inner peripheral side than in the prior art. That is, the diameter of the seal ring 58 can be smaller than in the prior art. In this way, if the diameter of the sealing ring 58 becomes smaller, the area where the first back pressure acts on the back surface of the end plate 31 is relatively reduced, so that the pushing force on the movable scroll 30 can be reduced. Therefore, the pressing force can be set lower than in the prior art, and the degree of freedom in designing the pressing force can be increased. As a result, an increase in thrust loss due to excess pressing force can be suppressed. the

In addition, the fixing member 50 of this embodiment is comprised from the case main body 51 and the ring member 71 fitted in this case main body 51. As shown in FIG. If the housing body 51 and the ring member 71 are integrally formed, the cutting tool interferes with the step 74 in the flange housing 54 when cutting the slit 59 , making the machining difficult. However, if the housing body 51 does not have the step 74 as shown in FIG. 2 , the cutting tool does not interfere with the housing body 51 , and the slit 59 can be easily formed by cutting. In addition, by fitting the ring member 71 into the housing body 51 , it is easy to obtain the fixing member 50 which is difficult to process. In addition, since the machining becomes easy, the shape accuracy of the fixing member 50 is improved, and the rotation operation of the scroll compressor 1 can be further stabilized. the

(Modification of the first embodiment)

(Modification 1)

The ring member 71 of the first embodiment has a notch formed by cutting the outer peripheral corner portion on the upper surface of the ring member 71 around the circumferential direction, but this method may be replaced. As shown in FIG. 3 , this In a modified example, a groove portion is formed in the upper surface of the ring member 71 along the circumferential direction, and the groove portion is used as the seal ring groove 57 . In the case of this modification, since the partition position of the back pressure space 100 can be set on the inner peripheral side, the pressing force is further reduced, and the increase in thrust loss due to excess pressing force is further suppressed. the

(Modification 2)

The flange portion accommodating portion 54 of the fixing member 50 of the first embodiment has a structure in which the ring member 71 is fitted into the housing body 51. However, as shown in FIG. 4 , the flange portion accommodating portion 54 of this modified example A part of the ring member 71 is integrally formed with the case main body 51 . In the case of this modified example, the opening on the side of the compression mechanism 10 of the flange portion housing portion 54 is formed by a portion corresponding to the opening of the ring member 71 of the first embodiment, and the opening diameter d2 and the outer diameter d1 of the slit 59 satisfy that d1 is larger than Equal to the relation of d2. For this reason, similarly to the first embodiment, an increase in thrust loss is suppressed. In addition, in this modified example, it is only necessary that the inner wall of the flange portion housing portion 54 is formed so as to satisfy the relationship that d1 is greater than or equal to d2. For example, the inner wall of the flange housing part 54 may have an inclined surface shape whose inner diameter becomes smaller from the bottom surface side of the flange housing part 54 to the compression mechanism 10 side in addition to the shape having the step 74 shown in FIG. 4 . . the

(Second Embodiment)

Next, the second embodiment of the present invention will be described in detail based on the drawings. In the present embodiment, the configuration of the flange portion accommodating portion 54 of the fixing member 50 is changed from the above-mentioned first embodiment. That is, in the first embodiment, the notch is formed only in the ring member 71 , but in the present embodiment, as shown in FIG. 5 , the notch is formed in both the ring member 71 and the case body 51 . the

Specifically, similarly to the first embodiment, in the ring member 71 , a cutout portion is formed around the entire circumferential direction at an outer peripheral corner portion of the upper surface of the ring member 71 . On the other hand, on the case main body 51 side, a notch portion is also formed around the entire circumferential direction at the inner peripheral corner portion of the upper surface. Moreover, the ring component 71 is embedded in the housing body 51 such that the upper surface of the ring component 71 and the upper surface of the housing body 51 are substantially on the same plane. The opening on the compression mechanism 10 side of the flange housing 54 is constituted by the opening of the ring member 71 . In this fitted state, the notches face each other to form an annular groove, and this annular groove becomes the seal ring groove 57 . That is, the seal ring groove 57 of this embodiment is formed around the circumferential direction across the upper surface of the ring member 71 and the upper surface of the housing body 51 . In addition, the cutouts of the ring member 71 and the housing body 51 may have various shapes obtained by cutting the corners other than the stepped shape provided at the corners as shown in FIG. 5 . the

In this way, also in the present embodiment, the partition position of the back pressure space 100 partitioned by the seal ring 58 can be provided on the inner peripheral side compared to the prior art without the ring member 71 . Therefore, the area on which the high pressure of the first back pressure space 101 acts can be reduced, and like the first embodiment, an increase in thrust loss can be suppressed. the

Also, since the flange housing portion 54 of the fixing member 50 of this embodiment is formed by fitting the housing body 51 into the ring member 71 as in the first embodiment, the slit 59 can be easily processed. Other structures, functions and effects are the same as those of the first embodiment. the

(third embodiment)

Next, the third embodiment of the present invention will be described in detail based on the drawings. This embodiment is configured by changing the configuration of the flange portion housing portion 54 of the fixing member 50 in the first embodiment. That is, in the first embodiment, the ring member 71 is formed with a notch, but in this embodiment, as shown in FIG. 6 , the case body 51 is formed with a notch. the

Specifically, the ring member 71 is a ring member having a quadrangular longitudinal section. On the other hand, in the housing body 51 , a notch is formed around the entire circumferential direction at the inner peripheral corner of the inner wall and upper surface of the recess 52 in which the ring member 71 is fitted. Moreover, the ring member 71 is embedded in the housing body 51 so that the upper surface of the ring member 71 and the upper surface of the housing body 51 are substantially on the same plane. Also in this embodiment, the opening on the side of the compression mechanism 10 of the flange housing portion 54 is formed by the opening of the ring member 71, and the opening diameter d2 and the outer diameter d1 of the slit 59 satisfy the relationship that d1 is greater than or equal to d2. In this fitted state, an annular groove is formed by the notch and the outer peripheral surface of the ring member 71 , and this annular groove becomes the seal ring groove 57 . In addition, the notch may be in various shapes formed by cutting the corners other than the stepped shape provided at the corners as shown in FIG. 6 . the

In this way, also in this embodiment, the partition position of the back pressure space 100 by the seal ring 58 can be provided on the inner peripheral side compared to the conventional system without the ring member 71 . Therefore, the area on which the high pressure of the first back pressure space 101 acts can be reduced, and like the first embodiment, an increase in thrust loss can be suppressed. the

Also, the flange housing portion 54 of the fixing member 50 of the present embodiment has a structure in which the housing body 51 is fitted into the ring member 71 as in the first embodiment, so the slit 59 can be easily processed. Other structures, functions and effects are the same as those of the first embodiment. the

(Fourth Embodiment)

Next, the fourth embodiment of the present invention will be described in detail based on the drawings. This embodiment is configured by changing the configurations of the flange portion housing portion 54 and the shaft support portion 56 of the fixing member 50 in the first embodiment. As shown in FIG. 7 , the fixing member 50 of this embodiment includes a housing body 51 having a through hole 60 penetrating from the center of the upper surface to the lower end with a certain diameter, and a cylindrical member is embedded in the lower part of the through hole 60 . 76. the

The cylindrical part 76 is pressed into the lower part of the through hole 60, and the bearing 55 is pressed into the inner peripheral side of the cylindrical part 76, and the upper end of the main shaft part 81 is supported by the bearing 55. rotate. That is, a shaft support portion 56 supporting the drive shaft 80 is formed on the lower portion of the fixing member 50, and the through hole 53 of the shaft support portion 56 is formed by the opening of the cylindrical member 76. On the other hand, the flange part 33 is accommodated in the upper part of the through hole 60, and the flange part accommodation part 54 is formed. The opening of the compression mechanism 10 side of the flange portion housing portion 54 is constituted by the upper portion of the through hole 60 . In addition, a seal ring groove 57 is formed in an annular shape outside the opening of the compression mechanism 10 side of the flange portion housing portion 54 on the end surface of the casing body 51 on the compression mechanism 10 side. the

On the outer peripheral side of the cylindrical member 76, a notch is formed around the entire circumferential direction. Also, a slit 59 is formed by the notch portion and the inner wall of the through hole 60 in which the cylindrical member 76 is fitted. In addition, the notch may be formed by cutting at least an outer peripheral corner of the upper surface of the cylindrical member 76 . In addition to the stepped shape shown in FIG. 7 , the shape of the notch may be any other shape obtained by cutting the outer peripheral corner. the

Thus, in the present embodiment, the slit 59 is formed by fitting the cylindrical member 76 which is a member different from the case main body 51 . Therefore, in the present embodiment, it is no longer necessary to cut the housing body 51 to form a groove to form a gap, and it is no longer necessary to enlarge the opening of the flange portion accommodating portion 54 so as not to interfere with the cutting tool. Therefore, in this embodiment, the opening of the compression mechanism 10 side of the flange portion housing portion 54 can be reduced, and thus the seal ring 58 supported by the seal ring groove 57 formed outside the opening can be reduced. In this way, also in this embodiment, the area where the high pressure of the first back pressure space 101 on the inner peripheral side of the seal ring 58 acts on the movable scroll 30 is relatively small, and the thrust loss is suppressed as in the first embodiment. increase. Other structures, functions and effects are the same as those of the first embodiment. the

(fifth embodiment)

Next, a fifth embodiment of the present invention will be described in detail based on the drawings. This embodiment is configured by changing the structure of the shaft support portion 56 of the fixing member 50 in the fourth embodiment. That is to say, the housing body 51 of the fourth embodiment has a cylindrical member 76 embedded in the through hole 60 having a certain diameter. However, in this embodiment, as shown in FIG. A cylindrical member 76 is embedded in the lower through-hole 60 having a large diameter. the

Specifically, the through hole 60 is composed of a lower hole 61 and an upper hole 62 formed continuously with the lower hole 61 and having a smaller diameter than the lower hole 61 . The cylindrical member 76 is fitted in and fixed to the lower hole 61 by press fitting. In addition, the cylindrical member 76 is provided with a notch formed by cutting the outer peripheral side of the cylindrical member 76 around the entire circumferential direction, as in the fourth embodiment. Also, a slit 59 is formed by the notch and the inner wall of the through hole 60 in which the cylindrical member 76 is fitted. In addition, the flange portion 33 is housed in the upper hole portion 62 to form a flange portion housing portion 54 . The opening of the compression mechanism 10 side of the flange portion housing portion 54 is constituted by an upper hole portion 62 . the

Thus, in the present embodiment, the cylindrical member 76 is fitted into the lower hole 61 having a larger diameter than the upper hole 62 forming the opening on the compression mechanism 10 side of the flange housing 54 . For this reason, in this embodiment, the opening on the side of the compression mechanism 10 of the flange portion receiving portion 54 is made smaller than in the fourth embodiment, so it is also possible to reduce the amount supported by the seal ring groove 57 formed on the outside of the opening. The sealing ring 58. In this way, in this embodiment, the action area of the high pressure of the first back pressure space 101 on the inner peripheral side of the seal ring 58 to the movable scroll 30 can be further reduced, and the effect of suppressing an increase in thrust loss can be increased. Other structures, functions and effects are the same as those of the fourth embodiment. the

(sixth embodiment)

Next, the sixth embodiment of the present invention will be described in detail based on the drawings. This embodiment is configured by changing the structure of the shaft support portion 56 of the fixing member 50 from the fourth embodiment. That is, in the fourth embodiment, the cylindrical member 76 is formed with a notch, but in this embodiment, as shown in FIG. 9 , the through hole 60 of the housing body 51 is formed with a notch. the

Specifically, the cylindrical member 76 is an annular member having a rectangular shape in longitudinal section. In addition, a groove portion is formed in an approximately central portion of the inner wall of the through hole 60 around the entire circumferential direction. In addition, the cylindrical member 76 is inserted into the through hole 60 so that its upper end is positioned at the opening of the groove, and is press-fitted and fixed. Further, a slit 59 is formed by the inner wall of the groove and the outer peripheral surface of the cylindrical member 76 facing the groove. In addition, the flange portion 33 is housed in the upper portion of the through hole 60 to form a flange portion housing portion 54 . The opening on the side of the compression mechanism 10 of the flange portion housing portion 54 is constituted by the upper portion of the through hole 60 . the

Thus, in the present embodiment, the slit 59 is formed by the groove portion provided on the inner wall of the through hole 60 , and the relationship between the outer diameter d1 of the slit 59 and the opening diameter d2 of the compression mechanism 10 side of the flange portion housing portion 54 is becomes d1 greater than d2. For this reason, in this embodiment, the opening diameter of the flange portion housing portion 54 on the side of the compression mechanism 10 can be made smaller than in the fourth embodiment in which the outer diameter of the slit 59 is equal. In this way, in this embodiment, the action area of the high pressure of the first back pressure space 101 on the inner peripheral side of the seal ring 58 to the movable scroll 30 can be relatively reduced, so the effect of suppressing an increase in thrust loss is increased. the

In addition, as shown in FIG. 9, the through hole 60 is a form in which grooves are provided on the inner wall of a through hole having a certain diameter, but it is not limited to this. For example, as in the fifth embodiment, an upper hole portion may be formed. The through-hole 60 having a smaller diameter than the lower hole 61 has a larger diameter, and a groove is formed on the inner wall of the lower hole 61 . Other structures, functions and effects are the same as those of the fourth embodiment. the

Claims (9)

1. A scroll compressor, comprising: a fluid compression mechanism (10) having a fixed scroll (20) and a movable scroll (30), and a flange on the back side of the movable scroll (30) The drive shaft (80) of the part (33) and the fixed member (50) arranged on the back side of the movable scroll (30) and forming a back pressure space (100) with the movable scroll (30), It is characterized by: On the fixing part (50), a flange part receiving part (54) and a through hole (53) are formed, and the flange part receiving part (54) is in the compression mechanism of the fixing part (50). (10) The end surface of one side is recessed in a circular shape in plan view and accommodates the flange portion (33) of the movable scroll (30), and the through hole (53) passes through the flange portion accommodation portion (54 ) bottom surface starts to extend, the drive shaft (80) is inserted into and supported by the through hole (53), A sealing ring groove (57) is provided on the end surface of the fixing member (50) on the side of the compression mechanism (10), and the sealing ring groove (57) is outside the opening of the flange part receiving part (54) formed in an annular shape, and supports a seal ring (58) that is in close contact with the back surface of the movable scroll (30) and divides the back pressure space (100) into an inner peripheral side and an outer peripheral side, An annular slit (59) is formed outside the through hole (53) on the bottom surface of the flange portion housing portion (54) of the fixing member (50), The outer diameter d1 of the slit (59) and the opening diameter d2 of the flange receiving portion (54) on the side of the compression mechanism (10) satisfy the relationship that d1 is greater than or equal to d2. 2. The scroll compressor according to claim 1, characterized in that: The opening on the side of the compression mechanism (10) of the flange portion housing portion (54) is configured such that a ring member (71) is fitted therein. 3. The scroll compressor according to claim 2, characterized in that: The seal ring groove (57) is constituted by a notch formed by cutting an outer peripheral corner of the upper surface of the ring member (71) around the entire circumferential direction. 4. The scroll compressor according to claim 2, characterized in that: The seal ring groove (57) is constituted by a groove portion formed by cutting the upper surface of the ring member (71) around the entire circumferential direction. 5. The scroll compressor according to claim 2, characterized in that: The seal ring groove (57) is formed by cutting the inner peripheral corner of the upper surface of the part where the ring member (71) is embedded in the flange part housing part (54) around the entire circumferential direction. . 6. The scroll compressor according to claim 2, characterized in that: The sealing ring groove (57) is composed of the upper surface that straddles the upper surface of the ring member (71) and the part where the ring member (71) is embedded in the flange part receiving part (54) around the entire circumference direction. Grooves formed on the surface. 7. The scroll compressor according to claim 1, characterized in that: The through hole (53) is configured to be embedded with a cylindrical member (76), At least the inner peripheral wall of the slit (59) is formed by the cylindrical member (76). 8. The scroll compressor according to claim 7, characterized in that: The slit ( 59 ) is formed by a notch formed by cutting the outer peripheral side of the cylindrical member ( 76 ) around the entire circumferential direction. 9. The scroll compressor according to claim 7, characterized in that: The slit ( 59 ) is formed by cutting the inner peripheral side of the portion where the cylindrical member ( 76 ) is embedded around the entire circumferential direction. the

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