CN103635694B - Compressor - Google Patents

Abstract

The compressor of the present invention is provided with an oil separation mechanism part (40) that separates oil from the refrigerant gas discharged from the compression mechanism part (10), and the oil separation mechanism part (40) includes: a cylindrical space that rotates the refrigerant gas (41); make the refrigerant gas discharged from the compression mechanism part (10) flow into the inflow part (42) of the cylindrical space (41); the refrigerant gas after the oil is separated from the cylindrical space (41) A delivery port (43) that sends out to a container inner space (31); and a discharge port ( 44). In addition, the cylindrical space (41) includes the projection of the delivery port (43), and when the diameter of the cylindrical space (41) is Do and the width of the inflow portion (42) is W, Do/2>W, Thereby, high efficiency of the electric motor unit (20), improvement of volumetric efficiency, and low oil circulation can be realized.

Description

compressor

technical field

The present invention relates to a compressor provided with an oil separation mechanism for separating oil from refrigerant gas discharged from the compression mechanism.

Background technique

In the prior art, compressors used in air conditioners, cooling devices, etc. generally have a compression mechanism part and a motor part for driving the compression mechanism part in the housing, and the refrigeration returned from the refrigeration cycle is compressed in the compression mechanism part. agent gas, which is sent to the refrigeration cycle. Usually, the refrigerant gas compressed in the compression mechanism part cools the motor part by passing through the motor part once, and then is sent into the refrigeration cycle through the discharge pipe provided in the case (for example, refer to Patent Document 1). . That is, the refrigerant gas compressed by the compression mechanism is discharged from the discharge port to the discharge space. Thereafter, the refrigerant gas is discharged to the upper portion of the motor space between the compression mechanism unit and the motor unit through the passage provided on the outer periphery of the frame. Part of the refrigerant gas is discharged from the discharge pipe after cooling the motor unit. In addition, other refrigerant gas, through the passage formed between the motor part and the inner wall of the housing, communicates with the motor space above and below the motor part, and after cooling the motor part, it enters through the gap between the rotor and the stator of the motor part. The motor space above the motor unit is discharged from the discharge pipe.

Prior art literature

patent documents

Patent Document 1: Japanese Patent Application Laid-Open No. 5-44667

Contents of the invention

The problem to be solved by the invention

However, in the conventional configuration, the high-temperature and high-pressure refrigerant gas compressed by the compression mechanism unit flows through the motor unit, so the motor unit is heated by the refrigerant gas, causing a problem in that the efficiency of the motor unit decreases.

In addition, through the passage provided on the outer periphery of the frame, the high-temperature exhaust gas flows through the lower part of the compression mechanism part, and the compression mechanism part is heated. In particular, the refrigerant gas in a low-temperature state returned from the refrigeration cycle is sent into the compressor through the suction path. The process in the chamber is heated. Therefore, when the refrigerant gas is sent into the compression chamber, the refrigerant gas has already expanded, and there is a problem that the circulation amount decreases due to the expansion of the refrigerant gas.

Furthermore, if the refrigerant discharged from the discharge pipe contains too much oil, there is a problem of deteriorating cycle performance.

The present invention was made to solve the above-mentioned conventional problems, and an object of the present invention is to provide a compressor that achieves high efficiency of the motor unit, improvement of volumetric efficiency, and low oil circulation.

method used to solve the problem

The compressor of the present invention is characterized in that: the oil separation mechanism has: a cylindrical space for rotating the refrigerant gas; an inflow portion for allowing the refrigerant gas discharged from the compression mechanism to flow into the cylindrical space; A discharge port for sending the final refrigerant gas from the cylindrical space to a space in one container; and a discharge port for discharging a part of the separated oil and refrigerant gas from the cylindrical space to the space in another container, wherein from In the case of upward projection, the area of the cylindrical space includes the area of the outlet, and when the diameter of the cylindrical space is Do and the width of the inflow portion is W, Do/2>W.

Accordingly, it is possible to provide a compressor capable of achieving high efficiency of the motor unit, improvement of volumetric efficiency, and low oil circulation.

The effect of the invention

According to the present invention, most of the high-temperature and high-pressure refrigerant gas compressed in the compression mechanism and sent out from the oil separation mechanism is introduced into the inner space of one container and discharged from the discharge pipe. Therefore, most of the high-temperature and high-pressure refrigerant gas does not pass through the motor unit, so the motor unit is not heated by the refrigerant gas, and the efficiency of the motor unit is improved.

In addition, according to the present invention, since most of the high-temperature and high-pressure refrigerant gas is introduced into the inner space of one container, heating of the compression mechanism part connected to the inner space of the other container can be suppressed, so that heating of the sucked refrigerant gas can be suppressed, A high volumetric efficiency in the compression chamber is obtained.

Furthermore, according to the present invention, the oil separated by the oil separation mechanism is discharged together with the refrigerant gas into another container inner space, so that almost no oil remains in the cylindrical space. Therefore, the separated oil is sent out from the delivery port together with the refrigerant gas without being blown up in the cylindrical space by the rotating refrigerant gas, and oil separation can be performed stably. In addition, since oil does not stagnate in the cylindrical space, the cylindrical space can be made compact.

In addition, according to the present invention, the high-temperature and high-pressure refrigerant gas flowing through the inflow portion can be efficiently introduced into the cylindrical space, and the fluid can be swirled in the cylindrical space without being disturbed.

Description of drawings

Fig. 1 is a longitudinal sectional view of a compressor according to Embodiment 1 of the present invention.

Fig. 2 is an enlarged sectional view of main parts of a compression mechanism unit in Fig. 1 .

3 is a plan view of an oil separation mechanism unit according to Embodiment 1 of the present invention.

4 is a graph showing the relationship of the oil circulation ratio to (Do-do)/2/W in the compressor according to Embodiment 1 of the present invention.

5 is an enlarged cross-sectional view of main parts of a compression mechanism unit in a compressor according to Embodiment 2 of the present invention.

6 is an enlarged cross-sectional view of main parts of a compression mechanism unit in a compressor according to Embodiment 3 of the present invention.

7 is an enlarged cross-sectional view of main parts of a compression mechanism unit in a compressor according to Embodiment 4 of the present invention.

Fig. 8 is a longitudinal sectional view of a compressor according to Embodiment 5 of the present invention.

Explanation of symbols

1 airtight container

2 oil storage

4 discharge pipe

10 Compression Mechanism Department

11 main bearing components

12 fixed scroll

17 outlet

19 silencer

20 Motor Department

31 container space

32 container space

33 Compression Mechanism Side Space

34 oil storage side space

40 Oil Separation Mechanism Department

41 cylindrical space

41a The first cylindrical space

41b second cylindrical space

41c The first cylindrical space

41d second cylindrical space

41e The first cylindrical space

42 inflow part

42a inflow part

42b inflow part

43 delivery exit

43a exit

43b exit

44 outlet

44a outlet

44b outlet

46 delivery tube

47 delivery tube

48 Refrigerant gas rotating parts

detailed description

The first invention resides in a compressor comprising a compression mechanism for compressing refrigerant gas and a motor for driving the compression mechanism in an airtight container, and the airtight container is divided into one container inner space and the other by the compression mechanism. The inner space of the container is provided with a discharge pipe for discharging the refrigerant gas from the inner space of one container to the outside of the airtight container, and the motor part is arranged in the inner space of the other container, wherein the compressor is also provided with the refrigerant gas discharged from the compression mechanism part. The oil separation mechanism part for gas separation oil, the oil separation mechanism part has: a cylindrical space for rotating the refrigerant gas; an inflow part for letting the refrigerant gas discharged from the compression mechanism flow into the cylindrical space; A discharge port for sending the final refrigerant gas from the cylindrical space to a space in one container; and a discharge port for discharging a part of the separated oil and refrigerant gas from the cylindrical space to the space in another container, wherein from In the case of upward projection, the area of the cylindrical space includes the area of the outlet, and when the diameter of the cylindrical space is Do and the width of the inflow portion is W, Do/2>W.

According to this configuration, most of the high-temperature and high-pressure refrigerant gas compressed in the compression mechanism and sent out from the oil separation mechanism is introduced into one container inner space and discharged from the discharge pipe. Therefore, most of the high-temperature and high-pressure refrigerant gas does not pass through the motor unit, so the motor unit is not heated by the refrigerant gas, and the efficiency of the motor unit is improved.

In addition, according to this configuration, since most of the high-temperature and high-pressure refrigerant gas is introduced into one container inner space, heating of the compression mechanism part connected to the other container inner space can be suppressed, so that the heating of the sucked refrigerant gas can be suppressed, and it is possible to obtain High volumetric efficiency in the compression chamber.

In addition, according to this structure, the oil separated by the oil separation mechanism is discharged together with the refrigerant gas from the discharge port opposite to the delivery port, so that almost no oil remains in the cylindrical space. Therefore, the separated oil is sent out from the delivery port together with the refrigerant gas without being blown up in the cylindrical space by the rotating refrigerant gas, and oil separation can be performed stably. In addition, since oil does not stagnate in the cylindrical space, the cylindrical space can be made compact.

In addition, according to the above configuration, the high-temperature and high-pressure refrigerant gas flowing through the inflow portion can be efficiently introduced into the cylindrical space, and the fluid can be swirled in the cylindrical space without being disturbed. Therefore, oil separation can be reliably performed in the cylindrical space.

The second invention is that, in the first invention, 0.4<(Do-do)/2/W<1.1 when do is the diameter of the delivery port.

According to this structure, the refrigerant gas introduced into the cylindrical space from the inflow groove is not directly sent out from the delivery port without rotation, and the delivery port area can be sufficiently ensured, so that the refrigerant gas can be reduced when passing through the delivery port. speed drops. That is, since the refrigerant gas can be reliably fed into the cylindrical space for oil separation and the refrigerant gas can be sent out from the delivery port with the flow velocity reduced, oil is not carried out from the delivery port.

A third invention resides in that, in the first or second invention, the compression mechanism section includes: a fixed scroll; a revolving scroll disposed opposite to the fixed scroll; and a main bearing that axially supports a shaft that drives the revolving scroll. Parts, a cylindrical space is formed in the fixed scroll and the main bearing part, and the discharge port communicates with the space in another container.

According to this structure, the oil separation mechanism part is formed in the compression mechanism part, the refrigerant gas flow path from the discharge port to the discharge pipe can be shortened, and the airtight container can be downsized.

Furthermore, according to this configuration, the oil separated by the oil separation mechanism is discharged together with the refrigerant gas into another container inner space, so that almost no oil remains in the cylindrical space.

A fourth invention resides in that, in any one of the first to third inventions, carbon dioxide is used as the refrigerant. Carbon dioxide is a high-temperature refrigerant, and the present invention is more effective when such a high-temperature refrigerant is used.

A fifth invention is that, in any one of the first to fourth inventions, an oil having polyalkylene glycol as a main component is used as the oil. Since the compatibility between carbon dioxide and polyalkylene glycol is low, the oil separation effect is high.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, this invention is not limited to this embodiment.

(implementation mode 1)

Fig. 1 is a longitudinal sectional view of a compressor according to Embodiment 1 of the present invention. As shown in FIG. 1 , the compressor of the present embodiment includes a compression mechanism unit 10 for compressing refrigerant gas and a motor unit 20 for driving the compression mechanism unit 10 in an airtight container 1 .

The inside of the airtight container 1 is divided into one container inner space 31 and the other container inner space 32 by the compression mechanism unit 10 . Furthermore, the motor unit 20 is arranged in another container inner space 32 . In addition, another tank inner space 32 is divided by the motor unit 20 into a compression mechanism side space 33 and an oil storage side space 34 . Furthermore, the oil reservoir 2 is arranged in the oil reservoir side space 34 .

In the airtight container 1 , the suction pipe 3 and the discharge pipe 4 are fixed by welding (welding). The suction pipe 3 and the discharge pipe 4 pass through the outside of the airtight container 1 and are connected to components constituting the refrigeration cycle. The suction pipe 3 introduces the refrigerant gas from the outside of the airtight container 1 , and the discharge pipe 4 leads the refrigerant gas out of the airtight container 1 from a container inner space 31 .

The main bearing component 11 is fixed in the airtight container 1 by welding, caulking (shrink fit) or the like, and supports the shaft 5 . A fixed scroll 12 is fixed to the main bearing member 11 with bolts. The orbiting scroll 13 engaged with the fixed scroll 12 is sandwiched between the main bearing member 11 and the fixed scroll 12 . The main bearing member 11 , the fixed scroll 12 and the orbiting scroll 13 constitute a scroll-type compression mechanism unit 10 .

Between the orbiting scroll 13 and the main bearing member 11 , a rotation limiting mechanism 14 is provided via an Oldham ring (Oldham ring) or the like. The rotation restriction mechanism 14 prevents the rotation of the orbiting scroll 13 and guides the orbiting scroll 13 to move in a circular orbit. The orbiting scroll 13 is eccentrically driven by an eccentric shaft portion 5 a provided on the upper end of the shaft 5 . By this eccentric drive, the compression chamber 15 formed between the fixed scroll 12 and the orbiting scroll 13 moves from the outer periphery to the center, reduces the volume, and compresses.

A suction path 16 is formed between the suction pipe 3 and the compression chamber 15 . The suction path 16 is provided on the fixed scroll 12 . In the central part of the fixed scroll 12, a discharge port 17 of the compression mechanism part 10 is formed. A reed valve 18 is provided at the discharge port 17 . A silencer 19 that covers the discharge port 17 and the reed valve 18 is provided on the side of one container inner space 31 of the fixed scroll 12 . The silencer 19 isolates the outlet opening 17 from a container interior 31 . The refrigerant gas is sucked into the compression chamber 15 from the suction pipe 3 through the suction path 16 . The refrigerant gas compressed by the compression chamber 15 is discharged from the discharge port 17 into the muffler 19 . The reed valve 18 is pressed open when the refrigerant gas is discharged from the discharge port 17 .

A pump 6 is provided at the lower end of the shaft 5 . The suction port of the pump 6 is disposed in the oil reservoir 2 provided at the bottom of the airtight container 1 . Pump 6 is driven by shaft 5 . Therefore, the oil in the oil storage part 2 can be reliably sucked up regardless of the pressure condition and the operating speed, and oil cut-off does not occur at the sliding part. The oil sucked up by the pump 6 is supplied to the compression mechanism unit 10 through the oil supply hole 7 formed in the shaft 5 . However, if the oil filter is used to remove foreign matter from the oil before or after pump 6 is sucked in, foreign matter can be prevented from being mixed into the compression mechanism unit 10, and further reliability can be achieved.

The pressure of the oil introduced into the compression mechanism portion 10 is substantially the same as the discharge pressure of the refrigerant gas discharged from the discharge port 17 , and becomes a source of back pressure against the orbiting scroll 13 . As a result, the orbiting scroll 13 moves away from the fixed scroll 12 in a stable manner without partial contact. Part of the oil seeks an escape place due to the supply pressure or its own weight, and generally enters the fitting portion of the eccentric shaft portion 5a and the orbiting scroll 13, and the bearing portion 8 between the shaft 5 and the main bearing member 11 to lubricate, and then falls. , return to oil storage part 2. A path 7 a is formed in the orbiting scroll 13 , one end of the path 7 a opens to the high-pressure region 35 , and the other end of the path 7 a opens to the back pressure chamber 36 . The rotation limiting mechanism 14 is arranged in the back pressure chamber 36 .

Therefore, part of the oil supplied to the high-pressure region 35 enters the back pressure chamber 36 through the path 7 a. The oil entering the back pressure chamber 36 lubricates the sliding portion and the sliding portion of the rotation limiting mechanism 14 , and applies back pressure to the orbiting scroll 13 through the back pressure chamber 36 .

Next, the oil separation mechanism part of the compressor of Embodiment 1 is demonstrated using FIG.1 and FIG.2. Fig. 2 is an enlarged cross-sectional view of a main part of a compression mechanism unit in Fig. 1 . The compressor of this embodiment is provided with an oil separation mechanism unit 40 that separates oil from refrigerant gas discharged from the compression mechanism unit 10 .

The oil separation mechanism part 40 has: a cylindrical space 41 that rotates the refrigerant gas; an inflow part 42 that communicates with the inside of the muffler 19 and the cylindrical space 41; 43; and the discharge port 44 communicating with the cylindrical space 41 and another container inner space 32. The cylindrical space 41 is composed of a first cylindrical space 41 a formed in the fixed scroll 12 and a second cylindrical space 41 b formed in the main bearing member 11 .

The inflow portion 42 communicates with the first cylindrical space 41a, and the opening of the inflow portion 42 is preferably formed on the upper end inner peripheral surface of the first cylindrical space 41a. Furthermore, the inflow portion 42 flows the refrigerant gas discharged from the compression mechanism portion 10 into the cylindrical space 41 through the muffler 19 . The inflow portion 42 opens in a tangential direction with respect to the cylindrical space 41 .

The delivery port 43 is formed on the upper end side of the cylindrical space 41 , and is formed on at least one container inner space 31 side from the inflow portion 42 . The delivery port 43 is preferably formed on the upper end surface of the first cylindrical space 41a. Further, the sending port 43 sends out the oil-separated refrigerant gas from the cylindrical space 41 to the single container inner space 31 .

The discharge port 44 is formed on the lower end side of the cylindrical space 41 , and is formed at least on the other side of the container inner space 32 than the inflow portion 42 . The discharge port 44 is preferably formed on the lower end surface of the second cylindrical space 41b. Furthermore, the discharge port 44 discharges the separated oil and a part of the refrigerant gas from the cylindrical space 41 to the compression mechanism side space 33 .

Here, the cross-sectional area A of the opening of the delivery port 43 is preferably smaller than the cross-sectional area C of the cylindrical space 41 and larger than the cross-sectional area B of the opening of the discharge port 44 . When the cross-sectional area A of the opening of the delivery port 43 is the same as the cross-sectional area C of the cylindrical space 41 , the swirling flow of refrigerant gas is blown out from the delivery port 43 without being directed toward the discharge port 44 . In addition, when the cross-sectional area B of the opening of the discharge port 44 is the same as the cross-sectional area C of the cylindrical space 41 , the swirling flow of refrigerant gas is blown out from the discharge port 44 . Furthermore, by making the cross-sectional area A of the opening of the delivery port 43 larger than the cross-sectional area B of the opening of the discharge port 44 , the flow path resistance of the delivery port 43 is reduced. As a result, the refrigerant gas flows more easily to the delivery port 43 than to the discharge port 44 . As an example, A/B can be set to about 9.

In this embodiment, the first cylindrical space 41 a is formed by drilling the outer peripheral portion of the fixed scroll 12 , and the second cylindrical space 41 b is formed by drilling the outer peripheral portion of the main bearing member 11 . In addition, on the end surface of the fixed scroll 12 opposite to the lap portion, a groove opening in a tangential direction with respect to the first cylindrical space 41 a is formed, and the side of the first cylindrical space 41 a is covered by the silencer 19 . A part of the groove, thereby constituting the inflow portion 42. Furthermore, the delivery port 43 is constituted by a hole formed in the muffler 19, and the hole is arranged at the opening of the first cylindrical space 41a. Moreover, the discharge port 44 is comprised by the hole formed in the bearing cap 45, and this hole is arrange|positioned at the opening of the 2nd cylindrical space 41b.

Hereinafter, the operation of the oil separation mechanism unit 40 of the present embodiment will be described. The refrigerant gas discharged into the muffler 19 is introduced into the cylindrical space 41 through the inflow portion 42 formed in the fixed scroll 12 . The inflow portion 42 is open in a tangential direction with respect to the cylindrical space 41 , so the refrigerant gas sent from the inflow portion 42 flows along the inner wall surface of the cylindrical space 41 and generates gas on the inner peripheral surface of the cylindrical space 41 . swirling flow. This swirling flow flows toward the discharge port 44 . The refrigerant gas includes oil supplied to the compression mechanism unit 10 , and while the refrigerant gas is rotating, oil with a high specific gravity adheres to the inner wall of the cylindrical space 41 by centrifugal force and is separated from the refrigerant gas.

The swirling flow generated on the inner peripheral surface of the cylindrical space 41 reaches the discharge port 44 or returns near the discharge port 44 to become an upward flow passing through the center of the cylindrical space 41 . The refrigerant gas from which the oil has been separated by the centrifugal force reaches the delivery port 43 by the upward flow, and is delivered to the inner space 31 of one container. The refrigerant gas sent to one container inner space 31 is sent out from the discharge pipe 4 provided in one container inner space 31 to the outside of the airtight container 1 and supplied to the refrigeration cycle.

In addition, the oil separated in the cylindrical space 41 is sent out from the discharge port 44 to the compression mechanism side space 33 together with a small amount of refrigerant gas. The oil sent to the compression mechanism side space 33 passes through the communication path between the wall surface of the airtight container 1 and the motor unit 20 due to its own weight, and reaches the oil storage unit 2 .

The refrigerant gas sent to the compression mechanism side space 33 passes through the slit of the compression mechanism unit 10 , reaches one container inner space 31 , and is sent out from the discharge pipe 4 to the outside of the airtight container 1 .

In the oil separation mechanism unit 40 of this embodiment, the delivery port 43 is formed closer to the one container inner space 31 side than the inflow portion 42 , and the discharge port 44 is formed closer to the other container inner space 32 side than the inflow portion 42 . Therefore, a swirling flow is generated on the inner peripheral surface of the cylindrical space 41 from the inflow portion 42 to the discharge port 44 , and a swirling flow is generated in the center of the cylindrical space 41 from the discharge port 44 to the delivery port 43 . and flow in the opposite direction. Therefore, as the discharge port 44 separates from the inflow part 42, the number of revolutions of the refrigerant gas increases, and the oil separation effect improves. In addition, since the swirled refrigerant gas passes through the center of the swirling flow, it is only necessary that the delivery port 43 be located on the side opposite to the discharge port from the inflow part 42 . That is, by making the distance between the inflow portion 42 and the discharge port 44 as large as possible, the effect of the oil rotational separation can be enhanced.

In addition, the oil separation mechanism unit 40 of this embodiment does not store the oil separated in the container inner space 32, and the oil is discharged from the discharge port 44 together with the refrigerant gas, so there is a problem that will be generated on the inner peripheral surface of the cylindrical space 41. The swirling flow is guided in the direction of the discharge port 44 .

Assuming that the discharge port 44 is not formed in the cylindrical space 41 and the oil stays in the cylindrical space 41, the flow leading to the outside from the discharge port 44 does not occur, so the swirling flow disappears before reaching the oil surface, or The oil will be rolled up when it reaches the oil surface. In addition, since the discharge port 44 is not formed in the cylindrical space 41 , it is necessary to form a sufficient space for storing oil in order to perform the oil separation function.

However, like the oil separation mechanism unit 40 of this embodiment, by discharging the oil from the discharge port 44 together with the refrigerant gas, the swirling flow can be guided to the discharge port 44 and the oil will not be caught.

According to the present embodiment, most of the high-temperature and high-pressure refrigerant gas compressed in the compression mechanism unit 10 and sent out from the oil separation mechanism unit 40 is introduced into one container inner space 31 and discharged from the discharge pipe 4 . Therefore, most of the high-temperature and high-pressure refrigerant gas does not pass through the motor unit 20, so the motor unit 20 is not heated by the refrigerant gas, and the efficiency of the motor unit 20 is improved.

In addition, according to the present embodiment, most of the high-temperature and high-pressure refrigerant gas is guided to the one container inner space 31, thereby suppressing heating of the compression mechanism part 10 in contact with the other container inner space 32, so that suction cooling can be suppressed. The heating of the agent gas results in a high volumetric efficiency in the compression chamber 15.

In addition, according to the present embodiment, the oil separated by the oil separation mechanism unit 40 is discharged to the other container inner space 32 together with the refrigerant gas, so that almost no oil remains in the cylindrical space 41 . Therefore, the separated oil is sent out from the delivery port 43 together with the refrigerant gas without being blown up in the cylindrical space 41 by the rotating refrigerant gas, and oil separation can be performed stably. Moreover, since oil does not stagnate in the cylindrical space 41, the cylindrical space 41 can be downsized.

In addition, according to the present embodiment, the oil reservoir 2 is disposed in the oil reservoir side space 34, and no oil is stored in the compression mechanism side space 33, so the airtight container 1 can be downsized. In addition, according to the present embodiment, the muffler 19 that isolates the discharge port 17 of the compression mechanism unit 10 from the inner space 31 of one container is arranged, and the inside of the muffler 19 and the cylindrical space 41 are communicated through the inflow portion 42, thereby achieving The refrigerant gas compressed by the compression mechanism unit 10 can be reliably introduced into the oil separation mechanism unit 40 . That is, since all the refrigerant gas passes through the oil separation mechanism part 40, oil can be efficiently separated from the refrigerant gas. In addition, most of the high-temperature refrigerant gas discharged from the discharge port 17 is discharged from the discharge pipe 4 to the outside of the airtight container 1 without passing through the other container inner space 32, so that the electric motor part 20 or the compression mechanism part can be suppressed. 10 is heated.

In addition, according to the present embodiment, since the cylindrical space 41 is formed in the fixed scroll 12 and the main bearing member 11, the flow path of the refrigerant gas from the discharge port 17 to the discharge pipe 4 can be formed relatively short, and the The airtight container 1 is miniaturized.

3 is a plan view of an oil separation mechanism unit according to Embodiment 1 of the present invention, viewed from the direction of a delivery port. The basic configuration of the present embodiment is the same as that disclosed in FIG. 1 , so description thereof will be omitted. In addition, the same structure as the structure demonstrated with FIG. 1 and FIG. 2 is attached|subjected with the same code|symbol, and a part of description is abbreviate|omitted.

In this embodiment, when projected from above, the area of the cylindrical space 41 includes the area of the delivery port 43, and when Do is the diameter of the cylindrical space 41 and W is the width of the inflow portion 42, Do satisfies /2>W relationship. In the case of Do/2<W, the refrigerant gas rises without rotating in the cylindrical space 41 and is sent out from the delivery port 43 . Since the refrigerant gas flows along the inner peripheral surface of the cylindrical space 41 , the relationship of Do/2>W is necessary for all the introduced refrigerant gas to rotate in the same direction. That is, by satisfying this relationship, the rotation separation function of the cylindrical space 41 can be effectively exerted.

In addition, in this embodiment, when the diameter of the delivery port 43 is do, the relationship of 0.4<(Do-do)/2/W<1.1 is satisfied. FIG. 4 is a graph showing the relationship of the oil circulation ratio to (Do-do)/2/W. As can be seen from FIG. 4 , with respect to (Do-do)/2/W, the oil circulation ratio becomes the minimum value within a certain range. In the area where (Do-do)/2/W is small, that is, in the area where (Do-do) is small, the cylindrical space 41 and the delivery port 43 have similar dimensions, and even if the refrigerant gas introduced from the inflow part 42 enters The cylindrical space 41 is sent out from the delivery port 43 without rotating. On the other hand, in a region where (Do-do)/2/W is large, that is, a region where (Do-do) is large, the delivery port 43 is extremely small relative to the cylindrical space 41, and the refrigerant gas after rotation passes through The speed when sending out the exit 43 is high. When the delivery speed is high, the oil separated in the cylindrical space 41 is rolled up and taken out from the delivery port 43 . According to the above content, (Do-do)/2/W has an optimal range. In addition, when the oil circulation ratio is large, the circulation performance is deteriorated. Specifically, oil adheres to the wall surface of the heat exchanger, causing heat transfer hindrance and lowering heat transfer efficiency. Let the oil circulation amount that does not affect the heat transfer efficiency be 100, and the vertical axis of FIG. 4 is the oil circulation amount ratio. That is, in order not to deteriorate the circulation performance, the oil circulation ratio needs to be 100 or less, preferably in the range of 0.4<(Do-do)/2/W<1.1 which should satisfy this.

(Embodiment 2)

5 is an enlarged cross-sectional view of main parts of a compression mechanism unit of a compressor according to Embodiment 2 of the present invention. The basic configuration of the present embodiment is the same as that disclosed in FIG. 1 , so description thereof will be omitted. In addition, the same structure as the structure demonstrated with FIG. 1 and FIG. 2 is attached|subjected with the same code|symbol, and a part of description is abbreviate|omitted.

In this embodiment, the first cylindrical space 41c and the delivery port 43a are formed by performing step hole processing on the outer peripheral portion of the fixed scroll 12 . The first cylindrical space 41 c is formed by machining a hole that does not pass through the end surface on the fixed surface side (the end surface on the lapping portion side) of the main bearing member 11 . The delivery port 43a penetrates from the end surface on the side of the connecting surface (the end surface on the side of the overlapping portion) with the main bearing component 11, or from the end surface on the side opposite to the fixed surface of the main bearing component 11 (the end surface on the side opposite to the overlapping portion), with a ratio of first The cylindrical space 41c is formed as a hole with a small cross section.

In addition, the second cylindrical space 41d and the discharge port 44a are formed by performing step hole processing on the outer peripheral portion of the main bearing member 11 . The second cylindrical space 41 d is formed by machining a hole that does not pass through the fixed surface (thrust receiving surface) of the fixed scroll 12 . The discharge port 44a penetrates through the second cylindrical space 41d from the fixed surface (thrust surface) with the fixed scroll 12, or from the fixed opposite surface (thrust surface) with the fixed scroll 12. formed by holes with small cross-sections.

In addition, the inflow portion 42a is formed to open in a tangential direction with respect to the first cylindrical space 41c from the end surface of the fixed scroll 12 on the side opposite to the fixed connection with the main bearing member 11 (the end surface on the side opposite to the lap portion). Through hole.

In this embodiment, the operation of the oil separation mechanism unit 40 is the same as that of the first embodiment, and the operation and effect are the same as those of the first embodiment, and description thereof will be omitted.

(Embodiment 3)

6 is an enlarged cross-sectional view of main parts of a compression mechanism unit of a compressor according to Embodiment 3 of the present invention. The basic configuration of the present embodiment is the same as that disclosed in FIG. 1 , so description thereof will be omitted. In addition, the same structure as the structure demonstrated with FIG. 1 and FIG. 2 is attached|subjected with the same code|symbol, and a part of description is abbreviate|omitted.

In this embodiment, a cylindrical delivery pipe 46 is provided in the cylindrical space 41 . One end 46 a of the sending pipe 46 forms the sending port 43 , and the other end 46 b of the sending pipe 46 is arranged in the cylindrical space 41 . However, in this embodiment, the other end 46b of the delivery pipe 46 extends into the second cylindrical space 41b. An annular space 46c is formed on the outer periphery of the delivery pipe 46, and the inflow portion 42 opens to the annular space 46c. At one end 46a of the delivery pipe 46, a flange 46d extending outward is formed.

The refrigerant gas flowing in from the inflow part 42 forms a swirling flow, passes through the annular space 46 c , reaches the discharge port 44 along the inner peripheral surface of the cylindrical space 41 , and then flows back through the center of the cylindrical space 41 . Then, it flows into the delivery tube 46 from the other end 46b of the delivery tube 46 and flows out from the one end 46a of the delivery tube 46 .

In the present embodiment, the first cylindrical space 41 e is formed by performing a stepped hole process on the outer peripheral portion of the fixed scroll 12 . That is, on the end surface of the fixed scroll 12 opposite to the lap portion, a hole having a cross-section larger than the inner circumference of the first cylindrical space 41e is formed, and the flange 46d of the delivery pipe 46 is accommodated in the hole. Here, the second cylindrical space 41 b is formed on the main bearing member 11 as in the first embodiment, but may be formed by processing a stepped hole on the outer periphery of the main bearing member 11 as in the second embodiment.

As shown in the present embodiment, by providing the delivery pipe 46 in the cylindrical space 41, for example, when the frequency of the compressor is increased, the oil separation effect can be reliably obtained. However, when the sending pipe 46 is provided, it is important that the axial center of the cylindrical space 41 coincides with the axial center of the sending pipe 46 .

In addition, when the sending pipe 46 is provided, a flange 46d is provided on the sending pipe 46, and the flange 46d is disposed in a hole formed in the cylindrical space 41, and the sending pipe 46 is fixed to the cylindrical space with the silencer 19. The cylindrical space 41 is important. In addition, the internal diameter cross-sectional area D of the delivery pipe 46 is larger than the cross-sectional area B of the discharge port 44 . As a result, the refrigerant gas flows more easily to the delivery port 43 than to the discharge port 44 . As an example, D/B can be set to about 9.

According to the present embodiment, the oil separation effect in the cylindrical space 41 can be enhanced by providing the cylindrical delivery pipe 46 in the cylindrical space 41 . In this embodiment in which the sending pipe 46 is provided, the basic operation of the oil separation mechanism unit 40 is the same as that of the first embodiment, and the operation and effect are the same as those in the first embodiment, and description thereof will be omitted.

(Embodiment 4)

7 is an enlarged cross-sectional view of main parts of a compression mechanism unit of a compressor according to Embodiment 4 of the present invention. The basic configuration of the present embodiment is the same as that disclosed in FIG. 1 , so description thereof will be omitted. In addition, the same structure as the structure demonstrated with FIG. 1 and FIG. 2 is attached|subjected with the same code|symbol, and a part of description is abbreviate|omitted.

In this embodiment, a cylindrical delivery pipe 47 is provided in the cylindrical space 41 . The delivery pipe 47 of this embodiment is integrally formed with the muffler 19 . One end 47 a of the sending pipe 47 forms the sending port 43 , and the other end 47 b of the sending pipe 47 is arranged in the cylindrical space 41 . However, in this embodiment, the other end 47b of the delivery pipe 47 extends into the second cylindrical space 41b.

An annular space 47c is formed on the outer periphery of the delivery pipe 47, and the inflow portion 42 opens to the annular space 47c. The refrigerant gas flowing in from the inflow portion 42 forms a swirling flow, passes through the annular space 47 c , reaches the discharge port 44 along the inner peripheral surface of the cylindrical space 41 , and then flows countercurrently through the center of the cylindrical space 41 . Then, it flows into the sending pipe 47 from the other end 47 b of the sending pipe 47 and flows out from the one end 47 a of the sending pipe 47 .

As shown in the present embodiment, by providing the delivery pipe 47 in the cylindrical space 41, for example, even when the frequency of the compressor is increased, the oil separation effect can be reliably obtained. In addition, when the sending pipe 47 is provided, it is important that the axial center of the cylindrical space 41 coincides with the axial center of the sending pipe 47 . Moreover, when the sending pipe 47 is provided, the sending pipe 47 can be fixed to the cylindrical space 41 by forming the sending pipe 47 integrally with the muffler 19 . In addition, the inner diameter cross-sectional area D of the delivery pipe 47 is larger than the cross-sectional area B of the discharge port 44 .

According to the present embodiment, the oil separation effect in the cylindrical space 41 can be enhanced by providing the cylindrical delivery pipe 47 in the cylindrical space 41 .

In this embodiment in which the delivery pipe 47 is provided, the basic operation of the oil separation mechanism unit 40 is the same as that of the first embodiment, and the operation and effect are also the same as those of the first embodiment, and description thereof will be omitted.

In addition, the cylindrical space 41 is composed of the first cylindrical space 41a formed in the fixed scroll 12 and the second cylindrical space 41b formed in the main bearing member 11 as in the first embodiment, but the second The cylindrical space 41b may also be formed by performing step hole processing on the outer peripheral portion of the main bearing member 11 as in the second embodiment.

(implementation mode 5)

Fig. 8 is a longitudinal sectional view of a compressor according to Embodiment 5 of the present invention. The basic configuration of the present embodiment is the same as that disclosed in FIG. 1 , so description thereof will be omitted.

In the present embodiment, the refrigerant gas rotating member 48 constituting the cylindrical space 41 is arranged in one container inner space 31 . The refrigerant gas rotating member 48 is provided on the outer peripheral surface of the muffler 19 . The refrigerant gas rotating member 48 is formed with an inflow portion 42b, a delivery port 43b, and a discharge port 44b.

The inflow portion 42b communicates with the interior of the muffler 19 and the cylindrical space 41 , the delivery port 43b communicates with the cylindrical space 41 and one container inner space 31 , and the discharge port 44b communicates with the cylindrical space 41 and one container inner space 31 . The opening of the inflow portion 42b is formed on the inner peripheral surface of the one end side of the cylindrical space 41 . Furthermore, the inflow portion 42 b flows the refrigerant gas discharged from the compression mechanism portion 10 from the inside of the muffler 19 into the cylindrical space 41 . The inflow portion 42b opens in a tangential direction with respect to the cylindrical space 41 .

The delivery port 43b is formed on one end side of the cylindrical space 41, and is formed on at least one end side of the inflow portion 42b. The delivery port 43b is preferably formed on the end surface of the cylindrical space 41 on the one end side. Furthermore, the delivery port 43b sends out the oil-separated refrigerant gas from the cylindrical space 41 to the one container inner space 31 .

The discharge port 44b is formed on the other end side of the cylindrical space 41, and is formed on at least the other end side of the inflow portion 42b. Moreover, the discharge port 44b is arrange|positioned facing the delivery port 43b. The discharge port 44b is preferably formed in the lower portion of the end surface on the other end side of the cylindrical space 41 . The discharge port 44b may also be formed on the side surface of the other end side of the cylindrical space 41 . Here, the so-called opposite includes not only the case where the discharge port 44 b is provided on the bottom surface of the cylindrical space 41 but also the case where it is provided on the side surface of the cylindrical space 41 . Furthermore, the discharge port 44b discharges the separated oil and a part of the refrigerant gas from the cylindrical space 41 to the one container inner space 31 . Here, the cross-sectional area A of the opening of the delivery port 43b is smaller than the cross-sectional area C of the cylindrical space 41 and larger than the cross-sectional area B of the opening of the discharge port 44b.

Hereinafter, the operation of the oil separation mechanism unit 40 of the present embodiment will be described. The refrigerant gas discharged into the muffler 19 is introduced into the cylindrical space 41 through the inflow portion 42 b formed on the upper surface of the muffler 19 . The inflow portion 42b is open in a tangential direction with respect to the cylindrical space 41, so the refrigerant gas sent from the inflow portion 42b flows along the inner wall surface of the cylindrical space 41, and is generated on the inner peripheral surface of the cylindrical space 41. swirling flow. This swirling flow is a flow going to the discharge port 44b. The refrigerant gas includes oil supplied to the compression mechanism unit 10 , and while the refrigerant gas is rotating, oil with a high specific gravity adheres to the inner wall of the cylindrical space 41 by centrifugal force and is separated from the refrigerant gas.

The swirling flow generated on the inner peripheral surface of the cylindrical space 41 becomes a reverse flow passing through the center of the cylindrical space 41 after reaching the discharge port 44 b or returning near the discharge port 44 b. The refrigerant gas from which the oil has been separated by centrifugal force reaches the delivery port 43 b due to the flow passing through the center of the cylindrical space 41 , and is delivered to the single container inner space 31 . The refrigerant gas sent to one container inner space 31 is sent out from the discharge pipe 4 provided in one container inner space 31 to the outside of the airtight container 1 and supplied to the refrigeration cycle.

In addition, the oil separated in the cylindrical space 41 flows down in one direction due to its own weight, and the discharge port 44b is formed in the lower part of the other end surface or the lower part of the cylindrical space 41, so that the oil is easily discharged. The separated oil is sent out from the discharge port 44b to the upper surface of the muffler 19 together with a small amount of refrigerant gas. The oil sent to the upper surface of the muffler 19 passes through the gap of the compression mechanism part 10 due to its own weight, reaches the compression mechanism side space 33 from a container inner space 31, and then passes through the wall surface of the airtight container 1 or the communication path of the motor part 20 to reach the Oil storage part 2. The refrigerant gas sent out from the discharge port 44b is sent out from the discharge pipe 4 provided in the inner space 31 of one container to the outside of the airtight container 1 and supplied to the refrigeration cycle.

In the oil separation mechanism unit 40 of this embodiment, the delivery port 43b is formed on one end side of the cylindrical space 41 rather than the inflow part 42b, and the discharge port 44b is formed on the other end side of the cylindrical space 41 than the inflow part 42b. . Therefore, a swirling flow is generated on the inner peripheral surface of the cylindrical space 41 from the inflow portion 42b to the discharge port 44b, and a swirling flow is generated in the center of the cylindrical space 41 from the discharge port 44b to the delivery port 43b. Flow in the opposite direction of flow. Therefore, as the discharge port 44b separates from the inflow part 42b, the number of rotations of the refrigerant gas increases, and the oil separation effect improves. In addition, since the swirled refrigerant gas passes through the center of the swirling flow, the delivery port 43b may be located on the side opposite to the discharge port from the inflow part 42b. That is, by making the distance between the inflow portion 42b and the discharge port 44b as large as possible, the effect of oil rotational separation can be enhanced.

In addition, the oil separation mechanism unit 40 of this embodiment does not store the oil separated in the cylindrical space 41, and the oil is discharged from the discharge port 44b together with the refrigerant gas, so that the oil on the inner peripheral surface of the cylindrical space 41 The swirling flow acts to guide the direction of the discharge port 44b.

Assuming that the discharge port 44b is not formed in the cylindrical space 41 and the oil stays in the cylindrical space 41, no flow leading to the outside from the discharge port 44b occurs, and the swirling flow entrains the oil. In addition, the discharge port 44b is not formed in the cylindrical space 41, and it is necessary to form a sufficient space for storing oil in order to exhibit the oil separation function. However, like the oil separation mechanism unit 40 of the present embodiment, by discharging the oil from the discharge port 44b together with the refrigerant gas, the swirling flow can be guided to the discharge port 44b, and the oil will not be caught.

According to this embodiment, rotation separation can be performed without changing the axial dimension of a compressor. In addition, since the number of rotations of the refrigerant gas increases, the cylindrical space 41 can be enlarged, and more specifically, the distance between the inflow portion 42b and the discharge port 44b can be increased. Thereby, the oil separation mechanism part 40 can be provided in the inside of the airtight container 1, maintaining the size of the compressor itself, and the oil rotation separation effect can be improved.

In addition, according to the present embodiment, by arranging the refrigerant gas rotating member 48 constituting the cylindrical space 41 in one container inner space 31, it is possible to shorten the flow path of the refrigerant gas from the discharge port 17 to the discharge pipe 4 and to seal the refrigerant gas. The container 1 can be downsized.

According to the present embodiment, the high-temperature and high-pressure refrigerant gas compressed in the compression mechanism unit 10 and sent out from the oil separation mechanism unit 40 is guided to one container inner space 31 and discharged from the discharge pipe 4 . Therefore, since the high-temperature and high-pressure refrigerant gas does not pass through the motor mechanism unit 20, the motor unit 20 is not heated by the refrigerant gas, and the efficiency of the motor unit 20 is improved.

In addition, according to the present embodiment, since the heating of the compression mechanism unit 10 connected to the other container inner space 32 can be suppressed by guiding the high-temperature and high-pressure refrigerant gas to the one container inner space 31, the heating of the sucked refrigerant gas can be suppressed, High volumetric efficiency can be obtained in the compression chamber 15 .

In addition, according to the present embodiment, the oil separated by the oil separation mechanism 40 is discharged together with the refrigerant gas into the single container inner space 31 , so that almost no oil remains in the cylindrical space 41 . Therefore, the separated oil is sent out from the delivery port 43b together with the refrigerant gas without being blown up in the cylindrical space 41 by the rotating refrigerant gas, and stable oil separation can be performed. Moreover, since oil does not stagnate in the cylindrical space 41, the cylindrical space 41 can be downsized. In addition, according to the present embodiment, the oil reservoir 2 is disposed in the oil reservoir side space 34, and no oil is stored in the compression mechanism side space 33, so the airtight container 1 can be downsized.

In addition, according to the present embodiment, the muffler 19 is arranged to isolate the discharge port 17 of the compression mechanism unit 10 from the inner space 31 of one container, and the inside of the muffler 19 and the cylindrical space 41 are communicated through the inflow portion 42b. The refrigerant gas compressed by the compression mechanism unit 10 can be reliably introduced into the oil separation mechanism unit 40 . That is, since all the refrigerant gas passes through the oil separation mechanism part 40, oil can be efficiently separated from the refrigerant gas. In addition, the high-temperature refrigerant gas discharged from the discharge port 17 is not discharged from the discharge pipe 4 to the outside of the airtight container 1 through the other container inner space 32 , so heating of the motor unit 20 and the compression mechanism unit 10 can be suppressed.

In the compressors in each of the above-mentioned embodiments, two or more cylindrical spaces 41 may be provided.

In addition, in the compressors of the above-described embodiments, carbon dioxide can be used as the refrigerant. Carbon dioxide is a high-temperature refrigerant, and the present invention is more effective when such a high-temperature refrigerant is used. In addition, when carbon dioxide is used as the refrigerant, it is preferable to use polyalkylene glycol-based oil (PAG) as the oil. PAG is a poorly soluble oil, and does not fuse with carbon dioxide refrigerant, but exists in a mixed state separated from each other. Therefore, when the refrigerant gas and PAG are introduced into the cylindrical space 41 , there is a large centrifugal force against the PAG having a high specific gravity of the refrigerant gas. As a result, PAG scatters in the outer peripheral direction, adheres to the inner wall of the cylindrical space 41, and can be separated from the refrigerant gas. That is, the effect of the present invention is more remarkable than that of poorly soluble oil (or immiscible oil).

Industrial availability

The present invention is applicable to scroll compressors, rotary compressors, etc., which have a compression mechanism unit and a motor unit in an airtight container, and is particularly suitable for compressors using high-temperature refrigerants.

Claims (5)

1. A compressor, characterized in that: A compression mechanism unit for compressing refrigerant gas and a motor unit for driving the compression mechanism unit are provided in the airtight container, The inside of the airtight container is divided into one container inner space and another container inner space by the compression mechanism part, A discharge pipe for discharging the refrigerant gas from the inner space of the one container to the outside of the airtight container is provided, and the motor unit is arranged in the inner space of the other container, wherein The compressor is further provided with an oil separation mechanism section that separates oil from the refrigerant gas discharged from the compression mechanism section, The oil separation mechanism part has: a cylindrical space for rotating said refrigerant gas; making the refrigerant gas discharged from the compression mechanism part flow into an inflow part of the cylindrical space; sending the refrigerant gas from which the oil has been separated from the cylindrical space to a delivery port of the inner space of the one container connected to the discharge pipe; and A part of the separated oil and refrigerant gas is discharged from the cylindrical space to a discharge port of the other container inner space where the motor part is arranged, wherein When projected from above, the area of the cylindrical space includes the area of the outlet, Furthermore, when Do represents the diameter of the cylindrical space and W represents the width of the inflow portion, Do/2>W. 2. The compressor according to claim 1, characterized in that: Assuming that the diameter of the delivery port is do, 0.4<(Do-do)/2/W<1.1. 3. The compressor according to claim 1 or 2, characterized in that: The compression mechanism part includes: fixed scroll; an orbiting scroll disposed opposite to the fixed scroll; and a main bearing member supporting a shaft driving said orbiting scroll, The cylindrical space is formed in the fixed scroll and the main bearing part, The discharge port communicates with the inner space of the other container. 4. The compressor according to claim 1 or 2, characterized in that: As the refrigerant, carbon dioxide is used. 5. The compressor according to claim 1 or 2, characterized in that: As the oil, an oil containing polyalkylene glycol as a main component is used.