WO2004092587A1

WO2004092587A1 - Enclosed compressor

Info

Publication number: WO2004092587A1
Application number: PCT/JP2004/005286
Authority: WO
Inventors: Takashi Morimoto; Hiroyuki Kawano; Hirofumi Yoshida
Original assignee: Matsushita Electric Industrial Co., Ltd.
Priority date: 2003-04-18
Filing date: 2004-04-14
Publication date: 2004-10-28
Also published as: JP2004316591A; JP4127108B2

Abstract

An enclosed compressor has a first discharge chamber (31) and a second discharge chamber (42). The first discharge chamber (31) is formed above a compression mechanism (2) by a muffler (77). The second discharge chamber (42) is formed by a compression mechanism portion including an enclosed container upper lid (76) inside an enclosed container (1) and the muffler (77). A volumetric ratio VR, a ratio of a volume V1 of the first discharge chamber (31) and a volume V2 of the second discharge chamber, is set to about 0.35 or less. Even when an enclosed compressor is downsized and its operating speed is increased, the structure above can enhance gas-liquid separation effect of oil and refrigerant gas.

Description

Specification

Hermetic compressor technical field

The present invention relates to a hermetic compressor used for refrigeration and air conditioning for business use, home use, or vehicles, or a refrigerator. Background art

A conventional hermetic compressor will be described with reference to Japanese Patent Application Laid-Open No. 2000-280252. To explain a conventional example, reference is made to FIG. 1 showing a hermetic scroll compressor according to the present embodiment.

The hermetic scroll compressor includes a compression mechanism 2, a motor 3 for driving a compression mechanism 2 provided below the compression mechanism 2, and a rotation mechanism of the And a crankshaft 4 for transmission to the engine. Furthermore, oil 6 for holding oil 6 held in an oil reservoir 20 provided at a lower portion in the closed container 1 is supplied to a bearing 66 of the crankshaft 4 and a sliding portion of the compression mechanism 2 through the crankshaft 4. It has mechanism 7.

In the scroll compressor having the above-described structure, the oil 6 is forcibly supplied to the bearing portion 66 and the sliding portion of the compression mechanism 2 against the gravity by the oil supply mechanism 7, so that a smooth operation can be ensured. The refrigerant gas 27 compressed by the compression mechanism 2 cools the electric motor 3 through a portion of the electric motor 3 in the closed container 1, and is then discharged out of the closed container 1. The oil supplied to the bearing part 66 and the sliding part of the compression mechanism 2 moves downward by the supply pressure and gravity and is naturally collected in the oil reservoir 20. At this time, since the refrigerant gas 27 always contacts the oil 6, the refrigerant gas 27 accompanies the oil 6 and brings in the oil when the refrigerant gas is supplied from the closed container to the refrigeration cycle. However, there is a problem that the pressure loss in the piping in the pipe and the heat exchange efficiency in the heat exchanger such as the condenser and the evaporator are reduced. An example of a conventional measure for solving the above problem will be described below. The first is that the collision of oil and the centrifugal separation of the refrigerant gas take place in the passage of the refrigerant gas from the compressor mechanism to the refrigerant gas discharged from the compressor to the outside of the closed container while cooling it through the motor. This is a method of designing so that the oil will not be accompanied by the refrigerant gas discharged to the outside of the closed container. Further, Japanese Patent Application Laid-Open No. 2000-280252 discloses the following invention with respect to the passage of the gas discharged from the compression mechanism 2. That is, the gas discharged from the compression mechanism 2 flows from the discharge chamber 31 in the container above the compression mechanism to the compression mechanism communication path 32, the communication path 34, the rotor path 36, the rotor lower chamber 35, the electric motor. A gas passage in the container is provided so that the gas passes through the lower part of 3, the stator passage 37, the stator upper chamber 38, and the external discharge port 39 in order, and is discharged out of the sealed container 1. Here, the compression mechanism communication passage 32 communicates from the discharge chamber 31 in the container to the lower part of the compression mechanism 2; the communication passage 34 extends from the compression mechanism communication passage 32 to the rotor upper chamber 33. The rotor passage 36 is provided in the rotor 3b so as to communicate the rotor upper chamber 33 and the rotor lower chamber 35; the stator passage 37 is a stator. 3a is provided between stator 3a or stator 3a and hermetically closed container 1 so that the lower and upper portions of 3a communicate with each other; stator upper chamber 38 corresponds to the outer peripheral area of communication path 34. The external discharge port 39 is provided at a height higher than the height of the stator upper chamber 38 in the closed container 1.

However, in the above conventional technology, although the gas-liquid separation effect of oil and refrigerant gas is improved, as the high-speed operation of a small hermetic compressor advances, the gas-liquid separation effect cannot be sufficiently achieved. Oil is discharged outside the compressor, causing a decrease in efficiency in the refrigeration cycle. Furthermore, as in the above-described conventional technology, only the arrangement around the electric motor and the refrigerant gas passage around the compression mechanism disposed below the compression mechanism in the closed vessel can reduce the size and speed of the hermetic compressor. There is a problem that the gas-liquid separation effect of oil and refrigerant gas has reached its limit. Disclosure of the invention

In order to solve the above-mentioned problems, a hermetic compressor of the present invention includes a hermetic container, a compression mechanism housed in the hermetic container, a motor disposed below the compression mechanism, having a rotor and a stator, and an electric motor. A crankshaft that transmits the rotational force of the oil to the compression mechanism, an oil reservoir that is provided in the lower part of the sealed container and accumulates oil, and an oil supply mechanism that supplies oil through the crankshaft to bearings, compression mechanism slides, and moving parts A hermetic compressor, wherein gas discharged from the compressor mechanism reaches a lower portion of the electric motor from a first discharge chamber formed by a muffler provided to cover an upper discharge port of the compression mechanism, Further rises, reaches the second discharge chamber formed by the closed container, the closed container upper lid, and the compression mechanism through the compression mechanism ascending passage, and then closes through the external discharge port provided above the compression mechanism. Outside the container It has a gas passage in the container to be discharged, and the ratio VR of the volume VI of the first discharge chamber VI to the volume V2 of the second discharge chamber VR, that is, the value obtained by dividing V1 by V2 is 0.35 or less (more preferably Is 0.3 or less). Further, the hermetic compressor of the present invention has a configuration in which the gas discharged from the compression mechanism reaches the lower part of the electric motor and the oil contained in the gas is separated in the gas passage in the container. Furthermore, the gas passage in the container was surrounded by a first discharge chamber, a compression mechanism communication path connecting the first discharge chamber to the lower part of the compression mechanism, and a passage force bar extending from the compression mechanism communication path to the upper part of the electric motor. A communication path, a descending passage provided in the motor so as to extend below the motor, an ascending passage provided in the electric motor so as to extend above the electric motor, and a compression mechanism or provided between the compression mechanism and the closed container. A gas passage comprising a compression mechanism ascending passage, a second discharge chamber formed of a sealed container, a closed container upper lid, and a compression mechanism, and an external discharge port provided at a position higher than the position of the compression mechanism. is there. With this configuration, even when a small hermetic compressor is operated at high speed, the gas-liquid separation effect between oil and refrigerant gas can be enhanced, and the hermetic seal can greatly reduce the amount of oil discharged from the compressor. A compact compressor can be provided. BRIEF DESCRIPTION OF THE FIGURES FIG. 1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention.

FIG. 2 is a diagram showing the oil discharge amount of the hermetic compressor.

FIG. 3 is a cross-sectional view of a hermetic compressor according to Embodiment 2 of the present invention.

FIG. 4 is a cross-sectional view of the hermetic compressor according to Embodiment 3 of the present invention.

FIG. 5 is a diagram showing an oil discharge amount in another configuration of the hermetic compressor.

FIG. 6 is a cross-sectional view of a hermetic compressor according to Embodiment 4 of the present invention.

FIG. 7 is a vertical sectional view of a main part of a hermetic compressor according to Embodiment 5 of the present invention. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(Embodiment 1)

FIG. 1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention. Hereinafter, an example of a hermetic compressor for a refrigeration cycle incorporating a vertical scroll type compression mechanism will be described.

The hermetic compressor according to the first embodiment of the present invention includes: a main bearing member 11 of a crankshaft 4 fixed in a hermetically sealed container 1 by welding or shrink fit by heat; It has a scroll-type compression mechanism 2 constituted by sandwiching a revolving scroll 13 that meshes with the fixed scroll 12 between the fixed scroll 12 and the fixed scroll 12 that is stopped above. Between the orbiting scroll 13 and the main bearing member 11, a rotation restricting mechanism 14 for preventing the orbiting scroll # 3 from rotating and guiding the orbiting scroll 3 to move in a circular orbit is provided, such as an Oldham ring. When the orbiting scroll 13 is eccentrically driven by the main shaft portion 4a at the upper end of the crankshaft 4, the orbiting scroll 13 orbits. By taking advantage of the fact that the compression chamber 15 formed between the fixed scroll 12 and the orbiting roll 13 becomes smaller while moving from the outer peripheral side to the central part, the suction pipe 1 that communicates with the outside of the closed vessel 1 The refrigerant gas sucked from 6 through the inlet 17 on the outer periphery of the fixed scroll 12 is compressed. Refrigerant gas that has exceeded the specified pressure is pushed into the closed container 1 by pushing and opening the reed valve 19 from the discharge port 18 at the center of the fixed scroll 12. Is discharged. The hermetic compressor according to Embodiment 1 of the present invention repeats a series of the above processes.

The lower end of the crankshaft 4 reaches the oil reservoir 20 at the lower end of the closed container 1, and is supported by the sub-bearing member 21 fixed in the closed container 1 by welding or shrink fitting, so that it can rotate stably. Can be. An electric motor 3 composed of a stator 3 a fixed to the closed casing 1 by welding or shrink fitting, and a rotor 3 b integrally connected around the middle of the crankshaft 4 includes a main bearing member 1 1 And the auxiliary bearing member 21. In addition, balance weights 23, 24 fixed by pins 22 are provided on the outer peripheral portions of the upper and lower end surfaces of the rotor 3b, whereby the rotor 3b and the crankshaft 4 rotate stably, The orbiting scroll 13 can be stably moved in a circular orbit.

The crankshaft 4 has an oil supply hole 26 formed in the axial direction. The oil supply mechanism 7 supplies the oil 6 in the oil reservoir 20 to the compression mechanism 2 through the oil supply hole 26 by a pump 25 driven by the lower end of the crankshaft 4, and a bearing part included in the compression mechanism 2. Oil 6 is supplied to 6 and each sliding part. The oil 6 supplied in this way flows out under the main bearing member 11 through the bearing portion 66 to drop into the oil reservoir 20 so as to obtain an escape space by the supply pressure or gravity, and finally the oil reservoir 20 Will be collected. Generally, the refrigerant gas 27 indicated by the broken arrow discharged from the compression mechanism 2 accompanies the oil 6 contacted in the compression mechanism 2 or the supplied oil 6 dripping under the main bearing member 11. And tends to accompany. With the conventional compressor, it is difficult to suppress the inclination, so that the oil 6 accompanying the refrigerant gas 27 cannot be sufficiently separated, and the oil is discharged together with the refrigerant gas discharged outside the closed container 1. Although there is a problem, this hermetic compressor has a gas passage A in the container to prevent the problem.

The in-vessel gas passage A is a passage for the refrigerant gas 27 discharged from the compression mechanism 2, from the in-vessel discharge chamber 31 above the compression mechanism 2 to the compression mechanism communication path 32, the communication path 34, Under the motor 3 through the rotor passage 36, the stator communication passage Ί2, and the rotor lower chamber 35 sequentially. And a passage configured to be discharged to the outside of the sealed container 1 via the stator passage 37, the stator upper chamber 38, the compression mechanism ascending passage 43, and the external discharge port 39 in this order. Say. The communication path 34 is surrounded by a path cover 51 so as to extend from the compression mechanism communication path 32 to the rotor upper chamber 33. Here, the compression mechanism communication passage 32 is a passage that communicates between the discharge chamber 31 in the container and the lower part of the compression mechanism 2; the communication passage 34 is a passage from the compressor structure communication passage 32 to the rotor upper chamber. The rotor passage 36 is a passage provided in the rotor 3b so that the upper rotor chamber 33 and the lower rotor chamber 35 communicate with each other; the stator communication path 7 Reference numeral 2 denotes a passage provided in the stator 3a so that the lower motor 3 including the upper stator chamber 38 and the lower rotor chamber 35 communicate with each other; the stator passage 37 is a passage of the stator 3a. A passage provided between the stator 3a or the stator 3a and the closed vessel 1 so as to communicate the lower part and the upper part; a stator upper chamber 38 is provided around the outside of the communication path 34; The mechanism raising passage 43 is provided in the compression mechanism 2; the external discharge outlet 39 is provided in the closed vessel 1 at a height equal to or higher than the height of the stator upper chamber 38. The in-vessel discharge chamber 31 of the in-vessel gas passage A and the compression mechanism communication path 32 are arranged on the outer peripheral side of the compression mechanism 2 and the bearing 66 thereof, and the refrigerant discharged from the compression mechanism 2 The gas 27 is collectively discharged into the communication path 34 below the compression mechanism 2. Subsequently, the communication path 34 guides the discharged refrigerant gas 27 to the rotor upper chamber 33. A part of the refrigerant gas 27 enters the rotor passage 36 in a state where it is gently swirled under the influence of the rotation of the rotor 3 b and the balance weight 23, passes through the rotor passage 36 downward, and separates the oil 6. Strongly collides with the separator. Due to the collision, the entrained oil 6 is effectively separated and the mist of the oil 6 drops and grows. In addition, since at least a part of the circumference of the space between the separation plate and the lower end of the rotor 3b is open to the side, centrifugal separation acts on the oil that has become droplets, and the oil 6 The separation effect is enhanced. Further, the remaining refrigerant gas 27 passing through the above-described descending passage is guided to the stator communication passage 72, where the oil 6 is formed into droplets and grown, thereby effectively performing gas-liquid separation. I have. The refrigerant gas 27 from which the oil 6 has been separated as described above passes through the stator passage 37 as a rising passage, and the stator upper chamber 3 8 further around the communication passage 34 around the bearing 66. Then, the air reaches the compression mechanism upper chamber 42 via the compression mechanism ascending passage 43 provided in the compression mechanism 2 and is discharged from the external discharge port 39 to the outside of the closed container 1. That is, since the refrigerant gas 27 from which the oil 6 has been separated does not come into contact with the refrigerant gas 27 accompanying the oil 6, the oil is discharged to the outside of the closed vessel 1 with the oil sufficiently separated. It can be supplied to a refrigeration cycle.

By the way, since the compression mechanism ascending passage 4.3 is provided in the compression mechanism 2 or between the compression mechanism 2 and the sealed container 1, it is difficult to make the passage area large. It is not easy to reduce the flow velocity of the refrigerant gas 27 ejected to the upper chamber 42. For this reason, when the hermetic compressor is operated at high speed and the circulation amount of the refrigerant gas 27 is increased, the flow velocity may reach several meters per second or more. The refrigerant gas 27 ejected from the compression mechanism ascending passage 43 collides with the closed container upper lid 76 at a considerable flow velocity, and its direction is forcibly changed. When the circulation amount of the refrigerant gas 27 is relatively small, the gas-liquid separation mechanism described above works effectively, and the oil 6 in the refrigerant gas 27 reaching the compression mechanism upper chamber 42 becomes very small. However, when the circulation amount of the refrigerant gas 27 increases, the residual ratio of the oil 6 also increases. When the refrigerant gas 27 collides with the upper lid 76 of the closed vessel at a considerable flow rate, the oil 6 in the refrigerant gas 27 is easily fragmented and atomized, and the outside of the closed vessel 1 is discharged from the external discharge port 39. Will be ejected. Hereinafter, the in-vessel discharge chamber 31 will be described as a first discharge chamber 31 and the compression mechanism upper chamber 42 will be described as a second discharge chamber 42.

Further, when the first discharge chamber 31 which is a discharge chamber in the container is formed in the second discharge chamber 42 which is the upper chamber of the compression mechanism above the compression mechanism 2, the second discharge chamber 42 is complicated. In many cases, the refrigerant gas 27 colliding with the top lid 76 of the closed vessel at a considerable flow velocity repeated revolving and rotating motions in the second discharge chamber 42 with a complicated shape. Thereafter, the liquid is discharged out of the closed container 1 through the external discharge port 39. In such a case, there is some correlation between the volume of the second discharge chamber 42 having a complicated shape and the volume of the first discharge chamber 31 related to the gas-liquid separation effect of the oil 6. Can be considered. Therefore, as a result of measuring the relationship between the volume ratio of both discharge chambers and the gas-liquid separation effect, it was experimentally revealed that the correlation between the two was not a complicated one but a relatively simple one.

Fig. 2 is a diagram showing the relationship between the volume ratio of the discharge chamber of the hermetic compressor and the gas-liquid separation effect, where the ratio of the volume of the first discharge chamber 31 to the volume of the second discharge chamber 42 is closed. It shows the oil discharge amount (wt%), which is the gas-liquid separation effect of the compressor 6 in the compressor.

In FIG. 2, the volume ratio VR is the volume VI occupied by the space of the first discharge chamber 31 formed by the compression mechanism upper surface and the muffler 77, and V 2 is the volume of the closed container lid 7 in the closed container 1. When the volume occupied by the space of the second discharge chamber 4 2 formed by the compression mechanism including the muffler 7 and the muffler 7 7, the value obtained by dividing ¥ 1 by ¥ 2, that is, the volume ratio VR = V 1 ZV 2

Curves ① and ② in FIG. 2 show the results obtained by changing the arrangement of the first discharge chamber 31.In each case, the volume ratio VR is 0.35, that is, VR = It can be seen that the oil discharge amount is rapidly increasing around 0.35. Thus, the volume ratio VR has a great influence on the gas-liquid separation effect of the oil 6. Therefore, when the first discharge chamber 31 is formed in the second discharge chamber 42 above the compression mechanism 2, it is preferable to set the volume ratio VR to 0.35 or less. More preferably, it is set to 3 or less. Based on the above measurement results, the hermetic compressor according to the first embodiment of the present invention has a configuration in which the first discharge chamber 31 is disposed in the second discharge chamber 42 above the compression mechanism 2, The configuration is such that the volume ratio VR = V12, which is the ratio between the volume VI of the first discharge chamber 31 and the volume V2 of the second discharge chamber 42, is set to 0.35 or less.

As described above, the hermetic-type compressor according to the first embodiment of the present invention has a configuration in which the volume ratio VR is set to be equal to or less than 0.35. Oil 6 in refrigerant gas 2 7 discharged outside should be minimized The oil 6 can be discharged to the outside of the closed vessel 1 and supplied to the refrigeration cycle in a state of being sufficiently separated. That is, even when a small hermetic compressor is operated at high speed, the gas-liquid separation effect of oil and refrigerant gas can be enhanced, and the amount of oil discharged from the hermetic compressor can be significantly reduced. it can.

(Embodiment 2)

FIG. 3 is a cross-sectional view showing a main part of the hermetic compressor according to Embodiment 2 of the present invention, and is a BB cross-sectional view of the hermetic compressor shown in FIG. The hermetic compressor according to the second embodiment of the present invention is characterized in that the first discharge chamber 31 is arranged eccentrically from the center of the compression mechanism 2, as shown in FIG. . Hereinafter, the hermetic compressor according to the second embodiment will be described with reference to FIG. 2 and FIG.

As described above, the curves ① and ② in FIG. 2 show the results of measuring the oil discharge amount with the arrangement of the first discharge chamber 31 changed. That is, the curve ① indicates a change in the oil discharge amount when the first discharge chamber 31 is arranged at the approximate center of the compression mechanism 2 in the radial direction of the sealed container 1. Curve ② indicates a change in the oil discharge amount when the first discharge chamber 31 is arranged eccentrically from the compression mechanism 2 in the radial direction of the sealed container 1. In particular, the curve た shows the change in the volume ratio VR with respect to the VR measured by measuring the oil discharge amount as a configuration in which the first discharge chamber 31 as shown in FIG. 3 is arranged eccentrically from the center of the compression mechanism 2. Things. Although not shown in FIG. 3, the external discharge port 39 is arranged at the approximate center of the compression mechanism 2.

As is clear from FIG. 2, the oil discharge amount is smaller when the first discharge chamber 31 is arranged eccentrically from the compression mechanism 2. The refrigerant gas 27 ejected from the compression mechanism ascending passage 43 collides with the upper lid 76 of the closed vessel at a considerable flow velocity, and the oil 6 in the refrigerant gas 27 is subdivided and atomized, and the second discharge chamber 4 It is considered that there is convection in the refrigerant gas 2, and the change in the convection of the refrigerant gas 27 changes depending on the arrangement of the first discharge chamber 31. Although the refrigerant gas 27 is finally discharged from the external discharge port 39 to the outside of the closed container 1, when the first discharge chamber 31 is arranged approximately at the center of the compression mechanism 2, the refrigerant gas 27 The convection time in the second discharge chamber 42 is reduced, and the liquid is discharged from the external discharge port 39 so as to be guided to the muffler 77 forming the first discharge chamber 31. As a result, the gas-liquid separation effect of the subdivided and atomized oil 6 is reduced, and the oil discharge amount is increased. Conversely, if the first discharge chamber 31 is disposed eccentrically from the compression mechanism 2, the convection time in the second discharge chamber 42 becomes longer due to less induction by the muffler 77, and the oil The gas-liquid separation effect of 6 is increasing. Thus, when the first discharge chamber 31 is formed in the second discharge chamber 42 above the compression mechanism 2, it is preferable that the first discharge chamber 31 be eccentrically arranged from the compression mechanism 2. is there.

As described above, in the hermetic compressor according to the second embodiment of the present invention, in the hermetic compressor in which the external discharge port 39 is arranged approximately at the center of the compression mechanism 2, the first discharge chamber 31 is connected to the compression mechanism 2. It is arranged at a position eccentric from the center, and as a result, a sealed type that optimally sets the volume ratio VR of the volume VI of the first discharge chamber 31 to the volume V2 of the second discharge chamber 42 Also in the compressor, it is possible to further enhance the gas-liquid separation effect of the oil 6.

(Embodiment 3)

FIG. 4 is a cross-sectional view showing a main part of the hermetic-type compressor according to Embodiment 3 of the present invention, and is a BB cross-sectional view of the hermetic-type compressor shown in FIG. The hermetic compressor according to the third embodiment of the present invention is characterized in that, as shown in FIG. 4, the first discharge chamber 31 is arranged at a position substantially opposed to the compression mechanism ascending passage 43. And

FIG. 5 is a diagram showing the relationship between the volume ratio of the discharge chamber and the gas-liquid separation effect, similarly to FIG. 2, and shows the ratio of the volume of the first discharge chamber 31 to the volume of the second discharge chamber 42. On the other hand, it shows the oil discharge (wt%), which is the gas-liquid separation effect of oil 6 of the hermetic compressor. Further, in FIG. 5, unlike the case of FIG. 2, the result of measuring the oil discharge amount by changing the positional relationship of the first discharge chamber 31 with respect to the compressor structure ascending passage 43 for the arrangement of the first discharge chamber 31 is shown. . Hereinafter, the hermetic compressor according to the third embodiment will be described with reference to FIG. 4 and FIG.

As shown in FIG. 4, the compression mechanism ascending passage 43 is usually formed on the outer peripheral portion of the compression mechanism 2, and the compression mechanism communication passage 32, the suction pipe 16, etc. It is difficult to configure the two equally. For this reason, as shown in the drawing, the compression mechanism ascending passage 43 is often arranged so as to be deviated in a certain direction in the radial direction of the closed casing 1.

Considering the arrangement of the compression mechanism ascending passages 43, the positional relationship with the first discharge chamber 31 was changed, and the result of measuring the oil discharge amount is shown in FIG.

In FIG. 5, the result of measuring the oil discharge amount by changing the arrangement of the first discharge chamber 31 with the configuration of the compression mechanism ascending passage 43 as shown in FIG. 4 is shown. Curves ③ and ④ in Fig. 5 show the results of measuring the oil discharge amount with the arrangement of the first discharge chamber 31 changed. Curve ③ indicates a change in the oil discharge amount when the first discharge chamber 31 is arranged at a position close to the compression mechanism ascending passage 43 in the radial direction of the closed casing 1. An example of the arrangement of the curve ③ is the configuration of the first discharge chamber 31 shown in FIG. 3 described above. In the curve ④, in the radial direction of the closed container 1, the first discharge chamber 31 is separated from the compression mechanism ascending passage 43 as much as possible as shown in FIG. The figure shows a change in the oil discharge amount in the case of the configuration arranged at the position. That is, as shown in FIG. 4, the first discharge chamber 31 is moved from the compression mechanism ascending passage 43 to the radial direction of the compression mechanism 2 with respect to the compression mechanism ascending passage 43 biased in a certain direction of the compression mechanism 2. It is configured so as to be separated from each other and to be located substantially opposite to each other.

As is clear from FIG. 5, the oil discharge amount is smaller when the first discharge chamber 31 is arranged as far as possible from the compression mechanism ascending passage 43. As described above, the refrigerant gas 27 ejected from the compression mechanism ascending passage 43 collides with the upper lid 76 of the closed vessel at a considerable flow velocity, and the oil 6 in the refrigerant gas 27 is subdivided and atomized. It is considered that convection occurs in the second discharge chamber 42. This refrigerant gas 27 The amount of the coolant gas 27 discharged from the external discharge port 39 directly to the outside of the closed container 1 without convection or the convection flow of 7 is determined by the arrangement of the first discharge chamber 31 and the compression mechanism ascending passage 43. This is the result of changing the relationship.

Although the refrigerant gas 27 is finally discharged from the external discharge port 39 to the outside of the closed container 1, if the first discharge chamber 31 is configured at a position relatively close to the compression mechanism ascending passage 43, (2) The amount of the refrigerant gas (27) discharged from the external discharge port (39) directly to the outside of the closed container (1) without convection in the discharge chamber (42) is increasing. This is because the muffler 77 constituting the first discharge chamber 31 has an effect of directly guiding the refrigerant gas 27 ejected from the compression mechanism ascending passage 43 to the external discharge port 39. Conversely, if the first discharge chamber 31 is moved away from the compression mechanism ascending passage 43, this effect is reduced.

In order to increase the gas-liquid separation effect of the oil 6, the muffler 77 is arranged as far as possible from the compressor structure ascending passage 43, in other words, at a position approximately opposite to the compression mechanism ascending passage 43. It is preferable to arrange them.

As described above, in the hermetic-type compressor according to the third embodiment of the present invention, the first discharge chamber 31 is located as far as possible from the compression mechanism ascending passage 43, and is disposed at a position substantially opposite to the compression mechanism ascending passage 43. Accordingly, even in a hermetic-type compressor in which the ratio VR of the volume V1 of the first discharge chamber 31 to the volume V2 of the second discharge chamber 43 is optimally set, It is possible to suppress the refrigerant gas 27 ejected from the compression mechanism ascending passage 43 from being directly discharged from the external discharge port 39, and to further enhance the gas-liquid separation effect of the oil.

(Embodiment 4)

FIG. 6 is a top view of the hermetic compressor according to Embodiment 4 of the present invention, and corresponds to the top view of the hermetic compressor shown in FIG. In FIG. 6, the dashed lines indicate the compression mechanism 2, the compression mechanism ascending passage 43, the muffler 77, the first discharge chamber 31, the compression mechanism communication passage 32, and the like. The hermetic compressor according to the fourth embodiment of the present invention is characterized in that, as shown in FIG. 6, the external discharge port 39 is arranged at a position substantially opposite to the compression mechanism ascending passage 43. And As shown in FIG. 6, in the fourth embodiment as well as in the third embodiment, the compressor structure ascending passage 43 is configured to be deviated in a certain direction with respect to the radial direction of the compression mechanism 2, and The discharge port 39 is arranged at a position as far as possible from the compression mechanism ascending passage 43, that is, at a position substantially opposite to the compression mechanism ascending passage 43. This configuration minimizes the refrigerant gas 27 ejected from the compression mechanism ascending passage 43 from being guided to the external discharge port 39. Therefore, even when the degree of freedom of the arrangement of the first discharge chamber 31 is low, the gas-liquid separation effect of the nozzle 6 is maximized by changing the arrangement of the external discharge ports 39. It becomes possible.

As described above, the hermetic-type compressor according to the fourth embodiment of the present invention has a configuration in which the external discharge port 39 is disposed at a position substantially opposite to the compression mechanism ascending passage 43, whereby the first discharge chamber 3 Even if the degree of freedom of the arrangement of 1 is low, the first discharge chamber is used to suppress the refrigerant gas 27 ejected from the compression mechanism ascending passage 43 from being directly discharged from the external discharge port 39. 3 The ratio of the volume of the volume VI of 1 to the volume V2 of the second discharge chamber 42 can be improved even in the hermetic compressor with the optimum VR set for the volume 6 of the oil 6. Become.

(Embodiment 5)

FIG. 7 is an enlarged longitudinal sectional view of a main part of a hermetic compressor according to Embodiment 5 of the present invention. The hermetic compressor according to Embodiment 5 of the present invention is characterized in that, as shown in FIG. 7, the first discharge chamber 31 is arranged at a position except immediately below the external discharge port 39. And Hereinafter, the hermetic compressor according to the fifth embodiment will be described with reference to FIG.

As shown in FIG. 7, in the fifth embodiment, the first discharge chamber 31 is not disposed immediately below the external discharge port 39 arranged on the closed container upper lid 76, that is, the external discharge port 39 The configuration is such that the first discharge chamber 31 is arranged at a position except immediately below. In the case of this configuration, the spatial distance between a part of the muffler 77 forming the first discharge chamber 31 and the external discharge port 39 can be set to the maximum. In the case where the first discharge chamber 31 is configured immediately below the external discharge port 39, to increase this space distance, the upper lid 7 of the closed container must be used. 6 has to be separated from the first discharge chamber 31 and there is a disadvantage that the overall height of the sealed container 1 becomes large. However, according to the fifth embodiment, the problem is small. When the above-mentioned space distance is increased, the same effect as that of setting the volume ratio VR in the first embodiment to a small value is obtained, and in the case where the design margin around the compression mechanism 2 is low, However, by considering the arrangement of the external discharge ports 39 having relatively high degree of freedom, it is possible to enhance the gas-liquid separation effect of the oil 6.

As described above, the hermetic-type compressor according to the fifth embodiment of the present invention has a configuration in which the first discharge chamber 31 is disposed at a position other than immediately below the external discharge port 39. Even when the design margin around the periphery is low, the same effect as when the volume ratio VR is set small can be obtained, and a hermetic compressor with improved oil-gas separation effect can be provided.

Industrial applicability

The present invention makes it possible for a hermetic compressor to discharge a refrigerant gas from which oil has been sufficiently separated out of a hermetic container even during high-speed operation, for business or home use, or for vehicles. It can be used as a hermetic compressor with an improved oil separation effect used in refrigeration, air conditioning, and refrigerators.

Claims

The scope of the claims

1. An airtight container, a compression mechanism housed in the airtight container, an electric motor arranged below the compression mechanism, having a rotor and a stator, and a crank for transmitting the rotational force of the electric motor to the compressor structure A hermetic compressor comprising: a shaft; an oil reservoir provided at a lower portion in the hermetic container, for accumulating oil; and an oil supply mechanism for supplying the oil to a bearing portion and a compression mechanism sliding portion through the crankshaft. ,

The gas discharged from the compression mechanism reaches a lower part of the electric motor from a first discharge chamber formed by a muffler provided so as to cover an upper discharge port of the compression mechanism, and further rises. Through a second discharge chamber formed by the closed container, the closed container upper lid, and the compression mechanism, and further discharged to the outside of the closed container through an external discharge port provided above the compression mechanism. Having a gas passage in the container,

A hermetic compressor characterized in that a volume ratio VR of the volume V1 of the first discharge chamber to the volume V2 of the second discharge chamber is set to 0.35 or less.

2. The hermetic seal according to claim 1, wherein the gas discharged from the compression mechanism in the gas passage in the container reaches a lower portion of the electric motor, and the oil contained in the gas is separated. Type compressor.

3. The gas passage in the container includes: the first discharge chamber; a compression mechanism communication path that communicates the first discharge chamber with a lower part of the compression mechanism; and a path that extends from the compression mechanism communication path to an upper part of the electric motor. A communication path surrounded by a cover; a descending passage provided in the electric motor so as to reach below the electric motor; an ascending passage provided in the electric motor so as to reach above the electric motor; and the compression mechanism or the compression mechanism. A compression mechanism ascending passage provided between a mechanism and the closed container; a second discharge chamber formed by the closed container, the closed container upper lid, and the compression mechanism; The external discharge provided in 3. The hermetic compressor according to claim 1, wherein the hermetic compressor is a gas passage including an outlet.

4. The external discharge port is disposed substantially at the center of the compression mechanism in the radial direction of the closed container, and the first discharge chamber is disposed at a position eccentric from the center of the compression mechanism. 4. The hermetic compressor according to claim 3, wherein:

5. The hermetic compressor according to claim 3, wherein the first discharge chamber is arranged at a position substantially opposed to the compression mechanism ascending passage in a radial direction of the hermetic container. .

6. The hermetic compressor according to claim 3, wherein the external discharge port is disposed at a position substantially opposed to the compression mechanism ascending passage in a radial direction of the hermetic container.

7. The hermetic compressor according to claim 3, wherein the first discharge chamber is arranged at a position except immediately below the external discharge port.