JP6193306B2 - Screw compressor and chiller unit including the same - Google Patents

Description

  The present invention relates to a screw compressor having an oil separator and a chiller unit including the same.

  A screw compressor used in a refrigeration cycle generally houses a male rotor (main rotor) and a female rotor (subrotor) that rotate substantially in parallel with each other, and the male and female rotors. Separation by a main casing (housing) having a bore, a discharge casing (housing wall) that abuts the rotor axial discharge side end surface of the main casing and covers the opening of the bore, a cylindrical vertical oil separator, and an oil separator And an oil sump for storing the collected oil.

  There is a centrifugal oil separator as a cylindrical oil separator. The centrifugal oil separator attaches oil to the wall surface by centrifugal force induced by the swirling flow in the separation space. The oil adhering to the wall surface flows down along the wall surface and is stored in an oil sump (oil sump chamber) provided in the lower part. In the centrifugal oil separator, the inflowing gas is generally configured to be discharged from the upper part of the separation space.

  As an example of separating and recovering oil contained in gas discharged from a compression mechanism portion of a compressor by a separation action using centrifugal force, there are cyclone separation systems disclosed in Patent Documents 1 and 2. In this conventional example, the gas and oil discharged from the compression mechanism are guided to a cyclone oil separation space provided in the upper portion of the oil tank, and the gas and oil are separated using centrifugal force.

Japanese Patent No. 4102891 JP 7-243391 A

  However, in this prior art, since the oil separator inlet passage is inserted into the space between the outer wall surface of the inner cylinder and the inner wall surface of the oil separator, the flow of gas flowing into the oil separation space from the introduction flow path, and the inner cylinder Flows swirling in the oil separation space between the outer wall surface and the inner wall surface of the oil separator collide with each other. Such a collision causes flow disturbance and the oil adhering to the inner wall of the oil separator resprays, and the flow is decelerated due to the collision. Oil spillage) increases.

  On the other hand, if the flow path cross-sectional area of the oil separator inlet passage is made small in order to avoid collision between the flows, the pressure loss of the inlet passage increases and the performance deteriorates. On the other hand, if the flow path cross-sectional area is increased in order to reduce pressure loss, the diameter of the oil separator must be increased in order to avoid collisions between the flows, and it is difficult to downsize the oil separator. there were.

  Furthermore, since the oil separation space between the outer wall surface of the inner cylinder and the inner wall surface of the oil separator forms a flow passage section that is long in the vertical direction, the flow of gas discharged from the introduction flow passage to the oil separation space spreads in the vertical direction. For this reason, the swirling flow decelerates during swirling and the oil separation efficiency decreases, and the swirling flow that spreads in the vertical direction collides with the oil level of the oil sump. Will increase. In addition, it is difficult to grasp the exact oil level position due to the deviation of the oil level.

  On the other hand, in order to avoid the collision of the swirling flow spreading to the oil surface, the height of the oil separator has to be increased, and it has been difficult to reduce the size of the oil separator.

  An object of the present invention is to provide a screw compressor that can reduce the amount of oil rising while achieving downsizing, and a chiller unit including the screw compressor.

In order to solve the problem, the screw compressor of the present invention has a male rotor and a female rotor that rotate while meshing with each other and the compression shaft is rotated, and a refrigerant discharged from the compression chamber flows in. An oil separator that separates the refrigerant into refrigerant gas and oil. The oil separator includes an outer cylinder, an inner cylinder positioned inside the outer cylinder, and refrigerant discharged from the compression working chamber. An introduction flow path that allows the inner wall surface to flow in a circumferential direction, and the upper end portion of the inner cylinder is held by the oil separator so that the outer wall of the inner cylinder is independent of the inner wall of the outer cylinder. The outer cylinder is provided with a guide part, and the guide part is configured such that the turning radius of the refrigerant turning in the guide part gradually decreases, and the refrigerant turning in the guide part spreads in the vertical direction. anda upper wall and lower wall restrains the, through the introduction passage The refrigerant that has flowed into the guide part swirls while being prevented from spreading in the vertical direction within the guide part, and then is discharged from the guide part and separated into gas refrigerant and oil by turning down along the inner wall of the outer cylinder. Then, the separated gas refrigerant flows into the inner cylinder from the lower end portion of the inner cylinder and rises, and the separated oil flows down along the inner wall surface of the outer cylinder.

  ADVANTAGE OF THE INVENTION According to this invention, the screw compressor which can reduce an oil climbing amount, achieving a size reduction, and a chiller unit provided with the same can be provided.

System diagram of refrigeration cycle Vertical section of screw compressor 2 is a cross-sectional view taken along line AA in FIG. BB cross-sectional view of FIG. Diagram showing the oil sump chamber Diagram showing guide tip shape Diagram showing guide tip shape Diagram showing guide tip shape Vertical section of screw compressor CC sectional view taken on line CC in FIG.

  A screw compressor of the present embodiment and a chiller unit using the same are related to a screw compressor having a cylindrical vertical oil separator and an oil sump for storing oil separated by the oil separator, and in particular, an air conditioner and a chiller unit. The present invention relates to a screw compressor that is used in an apparatus that constitutes a refrigeration cycle such as a refrigerator, and that reduces the amount of oil going up from the compressor (the amount of oil discharged outside the compressor).

Specifically, in the screw compressor of this embodiment, the rotation axis is substantially parallel and rotates while meshing with each other, the male rotor and the female rotor that form the compression working chamber, and the refrigerant discharged from the compression working chamber flows in, An oil separator that separates the refrigerant into refrigerant gas and oil. The oil separator includes an outer cylinder, an inner cylinder positioned inside the outer cylinder, and refrigerant discharged from the compression working chamber. An introduction flow path that allows the inner wall surface to flow in a circumferential direction, and the upper end portion of the inner cylinder is held by the oil separator so that the outer wall of the inner cylinder is independent of the inner wall of the outer cylinder. The outer cylinder is provided with a guide part, and the guide part is configured such that the turning radius of the refrigerant turning in the guide part gradually decreases, and the refrigerant turning in the guide part spreads in the vertical direction. anda upper wall and lower wall restrains the Guy via the introduction channel The refrigerant that has flowed into the part swirls while being prevented from spreading in the vertical direction in the guide part, and then is discharged from the guide part and is swung down along the inner wall of the outer cylinder to be separated into gas refrigerant and oil. The separated gas refrigerant flows into the inner cylinder from the lower end portion of the inner cylinder and rises, and the separated oil flows down along the inner wall surface of the outer cylinder.

  A screw compressor of the present embodiment and a chiller unit using the screw compressor will be described with reference to the drawings. FIG. 1 is a system diagram showing a refrigeration cycle (chiller unit) of the present invention. In FIG. 1, the refrigeration cycle is configured by connecting refrigerant pipes in order of a compressor 1, an oil separator 2, a condenser 3, an expansion valve 4, and an evaporator 5 to form a circulation cycle.

  When a large amount of oil supplied for lubrication of the bearings and screw rotors inside the compressor is mixed in the refrigeration cycle, the oil acts as a heat resistance in the evaporator 5 and the condenser 3 and inhibits heat exchange. Moreover, since the pressure loss increases due to the viscosity of the oil, the performance of the entire refrigeration cycle is degraded. Furthermore, if a large amount of oil flows out of the compressor 1 into the refrigeration cycle, the amount of oil held in the compressor decreases, and it is difficult to secure the amount of oil for lubricating the bearings and screw rotors inside the compressor. Become. Therefore, it is necessary to efficiently separate only the oil from the refrigerant gas compressed by the compressor 1 using the oil separator 2.

  FIG. 2 is a longitudinal sectional view of the screw compressor. In FIG. 2, the screw compressor includes a compressor body 1, motors 11 and 12 that drive the compressor body 1, and a motor casing 6 that houses the motors 11 and 12. The motor casing 6 forms a suction chamber (low pressure chamber) 29 on the side opposite to the compressor main body of the motors 11 and 12, and gas flows into the suction chamber 29 from the suction port 9 through the strainer 28. The motors 11 and 12 include a rotor 11 attached to a rotary shaft 27 and a stator 12 disposed on the outer peripheral side of the rotor 11. The stator 11 is fixed to the inner surface of the motor casing 6.

  The compressor main body 1 is connected to the motor casing 6, connected to the main casing 7 containing a male rotor 16 and a female rotor (not shown) that rotate while the rotary shaft 27 is parallel and meshing with each other, and connected to the discharge side of the main casing 7. The discharge casing 8 is provided.

  The main casing 7 is formed with a cylindrical bore 17 that accommodates the teeth of the male rotor 16 and the female rotor, and the rotor axial suction side of the bore 17 is opened. A suction port 15 is formed in the main casing 7 that forms this opening, and serves as a communication passage through which the suction gas immediately before compression flows to the teeth of the male rotor 16 and the female rotor. Furthermore, the bore 17 is also opened on the discharge side in the rotor axial direction. A radial discharge port 20 is formed in the main casing 7 that forms the opening, and an axial discharge port 21 is formed in the discharge casing 8, and a communication passage that allows the compressed refrigerant gas to flow into the discharge chamber 22. To do.

  The rotor axial suction side (the left side in FIG. 2) of the main casing 7 is connected to the motor casing 6. A gap between the rotor 11 and the stator 12 inside the motor casing 6 serves as a suction passage that allows the suction chamber 29 and the suction port 15 to communicate with each other.

  As shown in FIG. 2, the suction-side shaft portion of the male rotor 16 is supported by rolling bearings 13 and 14 disposed in the main casing 7, and the discharge-side shaft portion of the male rotor 16 is disposed in the discharge casing 8. It is supported by a rolling bearing 18 and a ball bearing 19. The suction-side shaft portion of the female rotor is supported by a rolling bearing (not shown) disposed in the main casing 8, and the discharge-side shaft portion of the female rotor is a roller bearing and ball bearing disposed in the discharge casing 8. (Not shown). In addition, 26 is an end cover which covers the outer side edge part of the bearing chamber which accommodates the roller bearing 18 and the ball bearing 19. FIG.

  The suction-side shaft portion of the male rotor 16 is directly connected to the rotation shaft 27 of the motors 11 and 12, and the male rotor 16 is rotated by driving the motors 11 and 12, and the female rotor is rotated while meshing with the male rotor 16. The gas compressed by the male rotor 16 and the female rotor flows out from the discharge ports 20 and 21 to the discharge chamber 22 formed in the discharge casing 8, flows from the discharge chamber 22 to the discharge passage 23 provided in the main casing 7, It is sent to the oil separator 2 via an introduction flow path 24 communicating with the discharge passage 23.

3 is a cross-sectional view taken along line AA in FIG. 2, and FIG. 4 is a cross-sectional view taken along line BB in FIG. 3, each of which is a cross-sectional view illustrating the internal configuration of the oil separator in this embodiment. . The oil separator 2 formed in the main casing 7 includes an introduction flow path 24 for introducing refrigerant gas into the oil separator, a throttle 30, guides 34, 38, and 48, an oil separator inner wall surface 36, an inclined surface (inclined portion). ) 47, the upper cover 44, the inner cylinder 35, the oil reservoir chamber 40 has a discharge port 10. The inner cylinder 35 configured in a cylindrical shape includes a flow path 37 between the inner wall surface 36 of the oil separator (outer cylinder) and the outer wall surface of the inner cylinder 35, and a part of the oil separator (outer cylinder). A swirl flow path (guide portion) 31 in which the refrigerant swirls is also formed between the inner wall surface of the guide 34 and the outer wall surface of the inner cylinder 35. The guide 34 does not reach the entire outer periphery, but is provided in a range of at least one-fourth of the inner cylinder 35 counterclockwise starting from at least the throttle 30 at the inlet flow passage outlet. The gas introduction flow path 24 may be clockwise.

Here, the inner wall of the outer cylinder of the oil separator decreases in diameter below the guides 34 and 38 through which the refrigerant swirls, and then gradually increases in diameter on an inclined surface (inclined portion) 47 toward the lower side , thereby expanding the end. It is configured in the shape of The lower end of the inner cylinder 35 is inserted between the start position and the end position of the inclined surface 47. The inner lid 35 is fixed to the upper lid 44, and is fastened to and integrated with the upper part of the oil separator. A refrigerant gas discharge port 10 is formed in the upper lid 44 of the upper part of the inner cylinder 35 of the oil separator 2.

  The refrigerant gas gradually descending while turning along the inclined surface 47 of the oil separator 2 is turned in the radial direction while turning along the curved surface 45 provided at the corner of the inner wall 35 on the guide 48 and the inner wall surface 36. Then, the flow direction is changed in the upward direction while turning back in the reversing chamber 42 between the lower end of the inner cylinder 35 and the guide portion 48 and flows into the inner cylinder 35. The refrigerant gas that has flowed into the inner cylinder 35 rises in the gas outlet channel 43 and is supplied from the discharge port 10 to the outside (for example, the condenser 3 constituting the refrigeration cycle) via the pipe (refrigerant pipe) 25.

  The oil separated by the oil separator 2 gradually approaches the wall surface due to the difference in centrifugal force resulting from the density difference with the refrigerant gas, and the wall surfaces (inner wall surfaces of the outer cylinder) 47, 36 of the oil separator 2; It adheres to the inner wall surface of the guide 34. The adhering oil flows down along the wall surface in the oil separator, is discharged from a circular oil drain hole 46 provided at the center of the guide 48, and is stored in an oil reservoir 40 formed below the oil separator. It is done. The oil stored in the oil reservoir 40 is subjected to the discharge pressure (high pressure) of the compressor body 1, while the bearings 13, 14, 18, 19 are almost under suction pressure (low pressure). Accordingly, the oil passes through the oil pipe 50 connecting the bearings 13, 14, 18, 19 and the oil reservoir 40 via the strainer 51 inserted into the oil reservoir 40, and the bearings 13, 14, 18, 19 are supplied to the meshing portion of the male / female screw rotor and act as a lubricant against the lubrication, the seal between the compression chambers, and the compression heat. Thereafter, the oil is again discharged together with the refrigerant gas, flows into the oil separator 2 and circulates inside the compressor.

  The screw compressor configured as described above operates as follows. The refrigerant gas and the oil mixed in the refrigerant gas after completion of the compression exit from the discharge ports 20 and 21 which are the openings of the compression chamber, flow through the introduction passage 24 through the discharge chamber 22 and flow into the oil separator 2. To do. Since the introduction flow path 24 is connected to the guide 34 in a tangential direction, the flow that has flowed into the oil separator 2 flows counterclockwise along the guide 34 that is a part of the oil separator wall surface. It flows into the passage 37. Since the flow path 37 is connected to the inversion chamber 42, the flow 33 gradually descends while swirling along the oil separator inner wall surface 36.

  Here, in the present embodiment, the diameter of the wall surface of the oil separator 2 (the inner wall of the outer cylinder) is configured so as to gradually decrease along the swirl flow path in which the refrigerant that has flowed in via the introduction flow path swirls. The refrigerant is separated into gas refrigerant and oil by swirling and descending along the swirl flow path that is the inner wall of the outer cylinder, and then the separated gas refrigerant flows into the inner cylinder from the lower end portion of the inner cylinder. The separated oil flows down along the inner wall surface of the outer cylinder. In particular, since the diameter of the wall surface of the oil separator 2 (inner wall of the outer cylinder) is configured to gradually decrease along the swirling flow path in which the refrigerant swirls, it is possible to suppress a decrease in the flow speed of the swirling refrigerant. Separation efficiency can be maintained.

  Here, when the outer wall of the inner cylinder is directly connected to the inner wall of the outer cylinder (oil separator 2), the connecting portion inhibits the swirling of the refrigerant, and the flow speed of the swirling refrigerant decreases. In the present embodiment, the upper end portion of the inner cylinder is held by the oil separator, so that the outer wall of the inner cylinder is independent of the inner wall of the outer cylinder and the inner cylinder is held by the oil separator. Therefore, since the connection part which connects the outer wall of an inner cylinder and the inner wall of an outer cylinder (oil separator 2) is not located in the turning flow path in which a refrigerant | coolant turns, the fall of the flow velocity of the turning refrigerant | coolant can be suppressed, and high oil Separation efficiency can be maintained.

  Further, when the gas flow 32 ejected from the introduction flow path 24 and the swirling gas flow 33 do not collide with each other when flowing into the oil separator from the introduction flow path 24, the gas flows 32 and 33 are connected to each other. May collide and slow down, disturbing the flow. In this case, the effect of centrifugal separation becomes weak, and the oil adhering to the wall surface is scattered again, so that high oil separation efficiency cannot be expected. Here, in the present embodiment, when flowing into the oil separator 2 from the introduction flow path 24, the oil separator so that the gas flow 32 ejected from the introduction flow path 24 and the swirling gas flow 33 do not collide with each other. The introduction flow path 24 is provided outside the circumferential surface of the inner wall surface 36, and the introduction flow path 24 is connected in the tangential direction of the oil separator 2. With such a configuration, the swirling flow flowing in from the introduction flow path 24 and the swirling gas flow 33 are less likely to collide, and the flow rates of the gases 32 and 33 can be maintained. Therefore, it can prevent that the effect of centrifugation falls and can maintain high oil separation efficiency.

  Further, when there is no guide 34 on the inner wall surface of the oil separator 2 when flowing into the oil separator from the introduction channel 24, the gas flow 32 ejected from the introduction channel 24 spreads in the vertical direction immediately after the inflow, There is a possibility that the swirling flow flowing around the cylinder 35 is decelerated. In this case, the effect of centrifugation is weakened and high oil separation efficiency cannot be expected. Here, in the present embodiment, a guide 34 is provided on the inner wall surface of the oil separator 2 so that the lower end of the cylindrical inner cylinder is inserted below the guide, and a flow path is provided between the guide and the inner cylinder. In this way, the gas flow 32 that has flowed into the guide 34 is blocked by the guide 34 and cannot spread in the vertical direction, so that a decrease in the flow velocity of the gas swirling in the guide 34 can be suppressed. . Further, the spread of the gas flow reaches the oil surface 41 and does not disturb the oil surface 41, so that the height of the oil separator can be reduced. Therefore, it is possible to prevent the centrifugal separation effect from being lowered, and it is possible to maintain a small size and high oil separation efficiency. The guide 34 is more effective when the height of the introduction channel 24 and the height of the guide 34 are the same, and the channel cross section is formed in a U-shape.

  Further, if the throttle 30 is not provided when flowing into the guide portion turning flow path 31, the flow 32 ejected from the introduction flow path 24 spreads in the horizontal direction immediately after the inflow, and the flow ejected into the guide may be decelerated. There is. In this case, the effect of centrifugation is weakened and high oil separation efficiency cannot be expected. Here, in the present embodiment, the gas flow 32 ejected to the oil separator 2 is temporarily increased at the throttle portion and is difficult to spread in the horizontal direction, so that the flow after the oil separator 2 is ejected is reduced. It can be suppressed and high oil separation efficiency can be maintained. Therefore, it can prevent that the effect of centrifugation falls and can maintain high oil separation efficiency. The restrictor 30 forms the restrictor 30 on the opposite vertical surface side of the guide 34 at the outlet portion of the introduction flow path 24, and the restrictor 30 is arranged so as to flow along the vertical surface of the guide 34, so that the flow is separated from the vertical surface. Since the vortex generated between the vertical surface and the flow 32 can be suppressed, high oil separation efficiency can be maintained.

  In addition, when flowing into the swirl flow path 31, the refrigerant flowing in the swirl flow path 31 unless the width of the swirl flow path 31 formed between the vertical surface of the guide 34 and the outer surface of the inner cylinder 35 is gradually reduced. Since the gas has friction with the wall surface and the swirling flow path 31 is wider than the flow path cross-sectional area of the introduction flow path 24, the flow velocity in the introduction flow path 24 cannot be maintained, and there is a possibility of decelerating rapidly. In this case, the effect of centrifugation is weakened and high oil separation efficiency cannot be expected. Here, in this embodiment, when the width of the swirl flow path 31 is gradually narrowed in the gas flow 32 direction, the cross-sectional area of the swirl flow path 31 is gradually reduced, so that the flow velocity of the gas flow 32 can be maintained. . Furthermore, since the gas flow 32 flowing in the guide is gradually swirled and discharged to the flow path 37, the flow velocity of the vertical component of the gas swirling and flowing in the flow path 37 is constant, so that uneven flow speed can be prevented. Therefore, it is possible to prevent the unevenness of the oil surface 41 and the re-scattering of the oil. Therefore, the height of the oil separator 2 can be reduced, and further, the effect of the centrifugal separation can be prevented from being reduced, so that the oil separator 2 is small and can maintain high oil separation efficiency. The guide 34 is more effective when the wall surface is formed of an arc.

  Further, if the guide 38 is not provided for the gas flow 33 around the inner cylinder 35, the swirling gas flow 33 enters the guide again and collides with the gas flow 32 flowing through the swirling flow path 31, and the gas flows. Flows 32 and 33 are decelerated and turbulent. Further, the gas flow that has entered the swirl flow path 31 re-scatters the oil flowing along the wall surface of the guide. Therefore, the effect of centrifugation is weakened, and the oil adhering to the wall surface is scattered again, which may reduce the oil separation efficiency. Here, in this embodiment, the guide 38 is provided so that the swirling gas flow 33 does not enter the guide 34 again. Thereby, since the swirling flow 33 comes to flow along the inner cylinder outer wall surface, the collision of the gas flows (32, 33) can be avoided and the flow velocity can be maintained. Therefore, it is possible to maintain a high oil separation efficiency by preventing the centrifugal separation effect from being lowered. It is more effective if the guide 38 forms an arc along the inner wall surface 36 of the oil separator.

  In addition, when the flow velocity of the flow descending while swirling is not reduced when flowing into the reversing chamber 42 from the flow path 37, there is a possibility that the flow of the refrigerant gas reaches the oil surface 41 and disturbs the oil surface 41. is there. In this case, re-scattering of the oil on the oil surface 41 and unevenness of the oil surface 41 occur, and high oil separation efficiency cannot be expected. Further, when the strainer 51 provided in the oil reservoir 40 is exposed from the oil surface due to the deviation of the oil surface 41, the refrigerant gas flows to the bearing through the strainer 51, so that the reliability is lowered due to insufficient lubrication of the bearing. . Here, in the present embodiment, the inner wall of the outer cylinder of the oil separator is configured to have a divergent shape by gradually increasing its diameter in an inclined portion that goes downward from the swirling flow path in which the refrigerant swirls. By providing a conical surface (inclined portion) 47 that widens in the direction of the oil surface 41 between the flow path 37 and the reversing chamber 42, the space that becomes the flow path of the refrigerant gas gradually widens, so that the flow velocity is reduced. be able to. Furthermore, by providing the conical surface 47, the surface area to which oil contained in the swirling refrigerant gas can adhere can be increased without extending the height of the oil separator. Therefore, the flow of the refrigerant gas can be prevented from reaching the oil surface 41, high oil separation efficiency can be maintained, and the height of the oil separator can be reduced. Further, if the space is suddenly widened to reduce the flow velocity without providing the conical surface (inclined portion) 47, the oil flowing down along the wall surface flows into the reversing chamber 42. As a result, the oil is re-scattered into the refrigerant gas swirling in the reversing chamber 42, and the pressure loss increases with the rapid expansion of the space, so that the compressor efficiency is lowered. In the present embodiment, the diameter of the inner wall of the outer cylinder is gradually increased at the inclined portion that goes downward from the swirling flow path in which the refrigerant swirls, so that the oil flowing down along the wall surface flows down along the curved surface 47 smoothly. In addition, since an increase in pressure loss can be suppressed, high oil separation efficiency can be maintained, and a reduction in compressor efficiency can be prevented.

  Further, between the reversing chamber 42 (the lower end portion of the inner cylinder) and the oil surface 41, a guide 48 (from the entire inner wall of the outer cylinder toward the inside, along the circumferential surface of the inner wall surface 36 of the oil separator, Is provided as an oil drain hole 46), the flow of the refrigerant gas descending while swirling flows along the guide 48, so that oil separation is performed while maintaining the flow of the refrigerant gas flowing down while swirling. The flow can be changed to a radial flow toward the center of the machine 2. Therefore, it becomes difficult for the refrigerant gas to flow into the oil drain hole 46, so that re-scattering and unevenness of the oil on the oil surface of the oil reservoir chamber 40 are suppressed. Furthermore, the strainer 51 provided at the lower part of the oil reservoir 40 is suppressed from being exposed from the oil surface 41 due to the deviation of the oil surface 41. Further, even when the refrigerant gas enters the oil reservoir 40 and disturbs the oil surface 41, the guide 48 acts as a partition, thereby preventing the re-scattered oil from flowing into the reversing chamber 42 again. Therefore, the flow of the refrigerant gas is prevented from reaching the oil level 41 and the oil level 41 is stabilized, so that high oil separation efficiency can be maintained, the reliability of the bearing is improved, and the height of the oil separator is increased. Can be lowered.

  In the present embodiment, the connecting portion of the guide 48 with the oil separator inner wall surface 36 is configured by the curved surface 45, so that the swirling and flowing flow smoothly flows along the curved surface 45, so that a vortex is hardly generated. Become. Therefore, the oil flowing down along the wall surface can be smoothly discharged into the oil discharge hole 46, so that high oil separation efficiency can be maintained.

  FIG. 8 is a view showing the guide tip shape. As shown in FIG. 8, the inner cylinder side surface of the guide to which the curved surface 45 is connected may be a conical surface formed with a gradient in the oil surface direction. Since the oil flowing along the curved surface flows down along the conical surface, the oil can be smoothly guided to the oil drain hole 46.

  Here, if the tip of the guide 48 provided with the oil drain hole 46 has an edge shape without providing a curved surface as the R portion, the surface tension that allows the oil flowing along the surface of the guide 48 to hold the oil at the edge portion is sufficient. Therefore, there is a possibility that the oil is re-scattered by the refrigerant gas flowing near the surface of the guide 48 and the oil separation efficiency is lowered. FIG. 6 is a view showing the guide tip shape. As shown in FIG. 6, if a curved surface serving as an R portion is provided at the tip of the guide 48, the oil flowing along the surface of the guide 48 sticks to the curved surface of the tip due to surface tension. Oil can flow down by gravity without being taken away. FIG. 7 is a view showing the guide tip shape. The tip of the guide 48 does not have to be a curved surface as shown in FIG. 6, and may be a conical surface as shown in FIG. 7, for example.

  As described above, when the circular oil drain hole 46 is provided at the center of the inner wall surface 36 of the oil separator 2 provided with the guide 48, the swirling refrigerant gas hardly enters the oil reservoir 40 through the oil drain hole 46. Become. Accordingly, the oil surface 41 is not disturbed by the flow of the refrigerant gas, and thus high oil separation efficiency can be maintained. In addition, with this configuration, the refrigerant gas does not easily enter the oil reservoir 40.

  The shape of the oil sump chamber 40 may not be a cylinder. FIG. 5 is a view showing the oil reservoir chamber. For example, as shown in FIG. 5, the shape of the oil reservoir 40 may be a rectangular parallelepiped. By comprising in this way, the height of an oil separator can be made low, maintaining high oil separation efficiency.

  In addition, when the shape of the oil drain hole is circular and the oil separator 2 is formed of a casting, manufacturing by casting or the like becomes easy.

  Further, the discharge port 10 of the oil separator 2 integrated with the compressor 1 is connected to the suction port 9 of the compressor 1 via the condenser 3, the expansion valve 4, and the evaporator 5 by a pipe 25 from FIG. 1. Therefore, the flow of the refrigerant gas swirling in the oil separator 2 rises while swirling in the reversing chamber 42 above the oil drain hole 46, so that the flow toward the center of the oil separator 2 rises in the reversing chamber 42. In doing so, gravity acts on the oil contained in the refrigerant gas, and the oil having a high density is separated downward (in the direction of the oil surface 41). Accordingly, if the oil drain hole 46 is provided at the center of the guide 48, the oil can be discharged to the oil reservoir chamber 40.

  FIG. 9 is a diagram showing another embodiment of FIG. As shown in FIG. 9, a circular partition plate 61 may be provided in a space between the inner cylinder 35 and the guide 48 (between the lower end portion of the inner cylinder and the oil drain hole). By providing a partition plate between the flow of oil and the flow of gas, the flow of gas and oil can be partitioned. Accordingly, since the space between the guide 48 and the partition plate 61 is filled with the oil flow, it is difficult for the swirling gas flow to flow into the oil drain hole 46. Accurate oil level position can be grasped with a sight glass or oil level gauge.

  FIG. 10 is a cross-sectional view taken along the line CC of FIG. 9 and is a cross-sectional view illustrating the internal configuration of the oil separator. As shown in FIG. 10, the partition plate 61 is fixedly supported by a round bar 62 connected to the inner cylinder 35, and the center of the partition plate 61 may be provided to be the center of the oil separator 2. It is more effective if the outer diameter of the partition plate is larger than the hole diameter of the oil drain hole 46.

  As described above, according to the present embodiment, it is possible to obtain a screw compressor that can reduce the amount of oil rising while achieving downsizing, and a chiller unit using the screw compressor.

1: compressor body, 2: oil separator, 3: condenser, 4: expansion valve, 5: evaporator, 6: motor casing, 7: main casing, 8: discharge casing, 9: suction port, 10: discharge Outlet, 11: Rotor, 12: Stator, 13, 14: Rolling bearing, 15: Suction port, 16: Male rotor, 17: Bore, 18: Rolling bearing, 19: Ball bearing, 20: Discharge port (radial direction ), 21: discharge port (axial direction), 22: discharge chamber, 23: discharge flow path, 24: introduction flow path, 25: pipe (refrigerant pipe), 26: end cover, 27: rotating shaft, 28: strainer, 29: Suction chamber, 30: Restriction, 31: Swirling flow path (guide portion), 32: Gas flow (jet flow), 33: Gas flow (swirling flow), 34: Guide (vertical surface), 35: Inner Cylinder, 36: inner wall surface (oil separator), 37: flow path (oil separator), 38: Id, 40: oil reservoir, 41: oil surface, 42: reversing chamber, 43: gas outlet channel (inside the inner cylinder), 44: upper lid, 50: piping (oil piping), 61: partition plate, 62: round rod

Claims (10)

A male rotor and a female rotor that rotate while meshing with each other with the rotation shafts being substantially parallel to each other to form a compression working chamber, and an oil separator that separates the refrigerant into refrigerant gas and oil through which refrigerant discharged from the compression working chamber flows. And comprising
The oil separator causes the outer cylinder, the inner cylinder located inside the outer cylinder, and the refrigerant discharged from the compression working chamber to flow in such a manner as to turn the inner wall surface of the outer cylinder in the circumferential direction. An introduction flow path,
By holding the upper end of the inner cylinder in the oil separator, the outer wall of the inner cylinder is held independently from the inner wall of the outer cylinder,
The outer cylinder includes a guide portion,
The guide portion includes a side wall configured to gradually reduce a turning radius of the refrigerant swirling in the guide portion, and an upper wall and a lower wall for suppressing the refrigerant swirling in the guide portion from spreading in a vertical direction. Have
The refrigerant that has flowed into the guide portion through the introduction flow path swirls while being prevented from spreading in the vertical direction in the guide portion, and is then discharged from the guide portion and swung along the inner wall of the outer cylinder. The refrigerant is separated into gas refrigerant and oil by descending, the separated gas refrigerant flows into the inner cylinder from the lower end of the inner cylinder and rises, and the separated oil flows along the inner wall surface of the outer cylinder. A screw compressor that flows down.   2. The screw compressor according to claim 1, wherein the guide portion has a U-shaped cross section formed by the side wall, the upper wall, and the lower wall.   3. The screw compressor according to claim 1, wherein the introduction flow path is connected in a tangential direction with respect to a circumferential direction of an inner wall of the outer cylinder.   4. The screw compressor according to claim 1, wherein the outlet portion of the introduction flow path has a convex throttle portion from a center of the outer cylinder toward an inner wall of the outer cylinder. 5. The screw compressor according to claim 1, wherein the outer cylinder has an inclined portion that increases in diameter as it goes downward from the guide portion .   The screw compressor according to any one of claims 1 to 5, further comprising an annular convex portion that extends downward from an inner wall of the outer cylinder toward an inner direction below a lower end of the inner cylinder. In Claim 5, it has the annular convex part which goes to the inner direction from the inner wall of the outer cylinder below the lower end of the inner cylinder,
The lower end portion of the inner cylinder is located between the upper end portion and the lower end portion of the inclined portion, and the convex portion is located below the lower end portion of the inclined portion.   The screw compressor according to claim 6 or 7, wherein an oil drainage hole is provided at a central portion of the convex portion.   The screw compressor according to claim 8, wherein a partition plate is provided between a lower end portion of the inner cylinder and the oil drain hole.   The chiller unit which connected the screw compressor, condenser, expansion valve, and evaporator in any one of Claims 1 thru | or 9 by refrigerant | coolant piping.

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