Screw compressor

Abstract

A screw compressor (100) is provided with a screw rotor (1), a housing (4) that houses the screw rotor (1), and a liquid supply mechanism (16, 41, 42, 43, 31) that supplies a liquid from a liquid injection nozzle (31) into a compression chamber (13) formed by the screw rotor (1) in the housing (4). The screw compressor (100) causes spray (30) injected from the liquid injection nozzle (31) to face the low-pressure side of the compression chamber (13).

Description

Technical Field

[0001] The present invention relates to a screw compressor. Background Art

[0002] A screw compressor is a device for compressing gas such as air. A screw compressor is a device that generates compressed gas by meshing two rotors, a screw-shaped male rotor and a female rotor.

[0003] However, in order to improve the gas compression efficiency in a screw compressor, a liquid supply mechanism for injecting liquid such as oil is provided in a gas compression chamber formed in a casing that accommodates male and female screw rotors. The injected liquid plays a role in cooling the compressed gas by exchanging heat with the liquid, and plays a role in sealing the gap between the screw rotors and the gap between the screw rotor and the casing to reduce gas leakage.

[0004] The technology of the conventional liquid supply mechanism into the gas compression chamber will be described.

[0005] Patent document 1 discloses a liquid supply mechanism, which generates a swirling flow inside the liquid supply mechanism while spraying, so that when the liquid is sprayed from the nozzle, the liquid is turned into tiny droplets under the action of the centrifugal force generated by the swirling flow. In addition, the compressed gas is cooled by heat exchange with the tiny droplets, or the gap between the screw rotors and the gap between the screw rotor and the casing is supplied with tiny droplets for sealing, thereby reducing gas leakage.

[0006] In addition, the adjustment device of the gas compressor lubrication system described in Patent Document 2 is equipped with a control device, which is configured to be connected to a temperature sensor and a pressure sensor. In addition, the control device continuously controls the valve mechanism of the liquid supply mechanism according to the temperature signal from the temperature sensor and the pressure signal from the pressure sensor. Through this control, the flow rate of the lubricant reaching the lubricant inlet of the compressor is continuously controlled to optimize the performance of the compressor. Thus, the control device controls the flow rate of the low-pressure gas reaching the compressor according to the pressure signal.

[0007] Prior art literature

[0008] Patent Literature

[0009] Patent Document 1: U.S. Patent Publication No. 2019 / 0093659A1

[0010] Patent Document 2: Japanese Patent No. 3712004 Summary of the invention

[0011] In order to cool the compressed gas and reduce gas leakage in the gaps between the screw rotors and between the screw rotors and the casing through the above-mentioned liquid supply mechanism, it is necessary to supply liquid that is suitable for (1) pressure changes and (2) shape changes in the compression chamber from the start of compression to the end of compression. However, the existing patent documents 1 and 2 have the following problems.

[0012] Regarding the problem of (1), the pressure difference between the injection pressure of the liquid injection nozzle and the pressure in the compression chamber decreases as the pressure in the compression chamber increases from low pressure to high pressure. Since the flow rate decreases if the pressure difference decreases, if the diameter of the liquid injection nozzle is not increased on the high-pressure side in accordance with the decrease in the pressure difference, the same liquid supply flow rate cannot be ensured. However, when the diameter of the liquid injection nozzle is increased, the size of the droplets increases, and the liquid is deteriorated into fine droplets. As a result, the uniform dispersion of the droplets in the compression chamber is reduced, and the cooling effect of the compressed gas cannot be fully obtained.

[0013] Regarding the problem (2), since the spray supplied from the liquid injection nozzle is non-directional and isotropically injected, it is not possible to supply the spray in a screw shape suitable for the compression chamber. Therefore, the effect of reducing gas leakage by sealing the gap between the screw rotors and the gap between the screw rotor and the casing with liquid droplets cannot be fully achieved.

[0014] The present invention has been made in view of the above-mentioned circumstances, and an object of the present invention is to provide a screw compressor capable of performing good internal cooling and sealing.

[0015] In order to solve the aforementioned problems, the screw compressor of the present invention includes: a screw rotor; a shell that accommodates the screw rotor; and a liquid supply mechanism that supplies liquid from a liquid injection nozzle into a compression chamber formed by the screw rotor in the shell, so that the spray injected from the liquid injection nozzle is directed toward the low-pressure side of the compression chamber.

[0016] Effects of the Invention

[0017] According to the present invention, it is possible to provide a screw compressor capable of performing good internal cooling and sealing. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 It is a longitudinal sectional view showing the structure of the screw compressor according to the first embodiment of the present invention.

[0019] Figure 2 The screw rotor Figure 1 Line II cross-sectional view.

[0020] Figure 3 The liquid supply method of the first embodiment Figure 2 View in direction II.

[0021] Figure 4 It is a schematic cross-sectional view showing the structure of the liquid supply portion of the jet nozzle.

[0022] Figure 5 yes Figure 4 A cross-sectional view of the liquid introduction flow path leading to the swirling flow generating portion, taken along line III-III.

[0023] Figure 6 yes Figure 4 A cross-sectional view of the swirl flow generating portion taken along line IV-IV.

[0024] Figure 7 It is a schematic cross-sectional view of the mechanism by which the spray has directivity.

[0025] Figure 8 This is a schematic cross-sectional view of liquid atomization in the liquid supply section on the low-pressure side.

[0026] Fig. 9 This is a schematic cross-sectional view of liquid atomization in the liquid supply section on the high-pressure side.

[0027] Fig.10 The liquid supply method according to the second embodiment of the present invention Figure 2 View in direction II.

[0028] Fig.11 The liquid supply method according to the third embodiment of the present invention Figure 2 View in direction II.

[0029] Fig.12 The liquid supply method according to the fourth embodiment of the present invention Figure 2 View in direction II.

[0030] Fig.13 The liquid supply method according to the fifth embodiment of the present invention Figure 2 View in direction II. DETAILED DESCRIPTION

[0031] Hereinafter, embodiments of the liquid supply mechanism for a screw compressor according to the present invention will be described with reference to the drawings.

[0032] In each figure, the same elements are marked with the same figure mark, and repeated descriptions are omitted. It should be noted that the present invention is not limited to the embodiments described below, and includes a variety of modified examples. For example, the embodiments described below are described in detail in order to clearly and easily explain the present invention, and are not necessarily limited to having all the structures. In addition, a part of the structure of a certain embodiment can be replaced with the structure of other embodiments, and in addition, the structure of other embodiments can be added to the structure of a certain embodiment. In addition, other structures can be added / deleted / replaced for a part of the structure of each embodiment.

[0033] <<First Embodiment>>

[0034] Figure 1 A schematic longitudinal sectional view showing the structure of a screw compressor 100 according to a first embodiment of the present invention. Figure 2 The screw rotor 1 is shown Figure 1 Line II cross-sectional view.

[0035] The screw compressor 100 according to the first embodiment is a device that compresses gas such as air.

[0036] The screw compressor 100 includes a screw rotor 1 (2, 3) for compressing gas and a housing 4 for accommodating the screw rotor 1. The screw rotor 1 has a male rotor 2 and a female rotor 3. The male rotor 2 and the female rotor 3 have teeth (blades) twisted into a screw shape and rotate in mesh with each other. It should be noted that the male rotor 2 and the female rotor 3 are collectively referred to as the screw rotor 1.

[0037] The screw compressor 100 includes a suction-side bearing 5 and a discharge-side bearing 6. The suction-side bearing 5 and the discharge-side bearing 6 support the male rotor 2 and the female rotor 3, respectively, so as to be rotatable.

[0038] A shaft seal member 7 such as an oil seal or a mechanical seal is provided at the lower end of the housing 4. The shaft seal member 7 seals between the housing 4 and the rotor shaft J.

[0039] Here, the “suction side” refers to the suction side of air or other gas (gas) in the direction of the rotor axis J of the screw rotor 1 (the suction port 14 side of the casing 4 ). The “discharge side” refers to the discharge side of gas in the axial direction of the screw rotor 1 (the discharge port 15 side).

[0040] <Male rotor 2, female rotor 3>

[0041] The suction-side end portion 2t of the male rotor 2 is connected to a motor 8 as a rotational drive source via a rotor shaft J.

[0042] like Figure 2As shown, a cylindrical male side hole (bore) 9 covering the male rotor 2 and a cylindrical female side hole 10 covering the female rotor 3 are formed on the inner surface of the shell 4. The male rotor 2 and the female rotor 3 are respectively accommodated in the shell 4 with a gap of several 10 to several 100 μm relative to the male side hole 9 and the female side hole 10 of the shell 4. There are two intersection lines between the male side hole 9 and the female side hole 10. The intersection line on the low-pressure side is defined as the suction side cusp (suction side intersection line) 11, and the intersection line on the high-pressure side is defined as the compression side cusp (compression side intersection line) 12.

[0043] Rotated by motor 8 ( Figure 2 The male rotor 2 (arrow α13) meshes with the female rotor 3 to rotate and drive the female rotor 3 ( Figure 2 α14).

[0044] Depend on Figure 2 The tooth grooves 2m of the male rotor 2 and the tooth grooves 3m of the female rotor 3 shown in the figure and the compression chamber 13 formed by the male side holes 9 and the female side holes 10 surrounding these tooth grooves are rotated by the male rotor 2 and the female rotor 3 ( Figure 2 The arrows α13 and α14) expand and contract. Figure 1 As shown, air or other gas is sucked in from the suction port 14 by the rotation of the male rotor 2 and the female rotor 3 ( Figure 1 The inhaled gas is compressed to a predetermined pressure and then discharged from the discharge port 15 ( Figure 1 α12).

[0045] In addition, liquid is injected into the compression chamber 13 from the outside of the screw compressor 100 through the liquid supply hole 16, the suction side bearing liquid supply hole 17 and the discharge side bearing liquid supply hole 18 (see Figure 2 ), suction side bearing 5, discharge side bearing 6 and shaft sealing component 7. The liquid is used for lubrication and sealing, and in most cases the liquid is oil.

[0046] The liquid plays the role of lubrication and sealing between the male rotor 2 and the female rotor 3, lubrication and sealing between the screw rotor 1 (2, 3) and the inner wall of the casing 4, lubrication and sealing between the shaft seal component 7 and the rotor shaft J, and lubrication of the suction side bearing 5 and the discharge side bearing 6.

[0047] <Liquid Supply Method>

[0048] Figure 3 The screw rotor 1 of the liquid supply method according to the first embodiment is shown. Figure 2 View in direction II.

[0049] A method of supplying liquid to the compression chamber 13 according to the first embodiment will be described.

[0050] Figure 3The arrow α21 in FIG. 1 indicates the direction of movement of the ridgeline 26 of the male rotor 2 and the ridgeline 27 of the female rotor 3. In other words, it indicates the direction of movement of the gas carried by the male rotor 2 and the female rotor 3. As the ridgelines 26 and 27 move, that is, as the gas moves, the compression chamber 13 (see FIG. 1 ) moves. Figure 2 ) pressure increase. That is, Figure 3 The downstream side of the upper side becomes the low-pressure side, and the upstream side of the lower side becomes the high-pressure side.

[0051] In order to cool the air (hereinafter, air is used as an example of gas) in the compression chamber 13 and seal each gap (the gap between the male rotor 2 and the female rotor 3, the gap between the screw rotor 1 (2, 3) and the inner wall of the casing 4), a gas is supplied to the compression chamber 13 (see Figure 2 ) sprays the spray 30, which is a state where the liquid (mostly oil) is atomized from the spray nozzle 31. The spray 30 is formed to supply the liquid (mostly oil) to the space inside the housing 4 without omission.

[0052] The present embodiment (invention) is characterized in that the spray 30 is injected toward the low-pressure side of the compression chamber 13. As a result, the droplets of the spray 30 spread from the low-pressure side to the high-pressure side, and the time they stay in the compression chamber 13 becomes longer. As a result, the cooling and sealing properties of the space inside the housing 4 are improved, and the compression efficiency of the air (gas) can be improved.

[0053] In addition, Figure 3 The invention is characterized in that the spray 30 injected from the liquid injection nozzle 31 (31a, 31b, 31c) is directed in a direction orthogonal to the ridgeline 26 on the positive side and the ridgeline 27 on the negative side of the screw rotor 1 (the direction of the spray 30 is the low-pressure side of the compression chamber 13).

[0054] Figure 4 A schematic cross-sectional view showing the configuration of a liquid supply portion of the injection nozzle 31 (31a, 31b, 31c). Figure 4 The arrows in the figure indicate the flow of liquid.

[0055] The liquid spray nozzle 31 (31a, 31b, 31c) forms the spray 30 by centrifugal force. Therefore, by making the central axis 31o (refer to Figure 4 ) is inclined and directional.

[0056] like Figure 3 As shown, by directing the spray 30 toward a direction perpendicular to the ridgeline 26 on the male side and the ridgeline 27 on the female side of the screw rotor 1 (having directivity), the spray 30 is diffused without omission left and right with the line perpendicular to the ridgeline 26 on the male side and the ridgeline 27 on the female side as the center. Therefore, the spray supply corresponding to the spatial shape of the inclined compression chamber 13 unique to the screw compressor 100 can be achieved.

[0057] <Liquid injection nozzle 31 from the low pressure side to the high pressure side of the compression chamber 13>

[0058] A further feature of this embodiment (invention) is that the diameter Φ (refer to Fig. 9 ) increases as it moves from the low-pressure side to the high-pressure side of the compression chamber 13, and the swirling flow in the injection hole is enhanced (the pressure increases). Figure 3 The high pressure side of the injection nozzle 31 shown (see Fig. 9 ) has a larger nozzle diameter Φ than the low pressure side (refer to Figure 8 ). This is because, in the past, there was a problem that the pressure difference between the liquid supply pressure and the liquid injection nozzle became smaller as the pressure went toward the high pressure side of the compression chamber, thereby reducing the liquid supply flow rate. Figure 3 In the example, the cross section of the nozzle hole becomes an ellipse because the nozzle hole is oriented in an oblique direction (inclined toward the low-pressure side).

[0059] Therefore, in this embodiment (invention), the amount of spray 30 on the high pressure side is increased by increasing the diameter of the injection hole of the injection nozzle 31 from the low pressure side to the high pressure side. This can prevent the liquid supply flow rate from decreasing on the high pressure side of the compression chamber 13.

[0060] It should be noted that in the conventional configuration, when the diameter of the injection hole of the injection nozzle is increased, the amount of liquid increases and the atomization of the liquid decreases, which causes a problem that cooling and sealing properties decrease.

[0061] Therefore, in the present embodiment (invention), the swirling flow in the spray hole of the liquid of the spray nozzle 31 (31a, 31b, 31c) on the high pressure side is enhanced compared to the low pressure side. By enhancing the swirling flow in the spray hole of the spray nozzle 31 (31a, 31b, 31c) of the liquid, even if the spray hole diameter Φ of the spray nozzle 31 (31a, 31b, 31c) becomes larger, it is possible to prevent the liquid from being reduced in atomization.

[0062] <Structure of Liquid Supply Mechanism Including Injection Nozzle 31 for Enhancing Swirling Flow>

[0063] use Figures 4 to 9 The diameter Φ (refer to FIG. 1 ) of the injection hole of the injection nozzle 31 ( 31a , 31b , 31c ) is increased from the low pressure side to the high pressure side of the compression chamber 13. Figure 4 ) is increased and the swirling flow in the spray hole (in the spray nozzle 31) is strengthened.

[0064] from Figure 4 The liquid supplied from the oil supply hole 16 shown in FIG. 1 is introduced into the liquid flow path 41 (see FIG. Figure 5) flows into the swirl flow generating section 42 (refer to Figure 6 ). Figure 5 Show Figure 4 4 is a cross-sectional view of the liquid introduction flow path 41 leading to the swirl flow generating portion 42, taken along line III-III.

[0065] The liquid introduction channel 41 is divided into two channels by a channel separation wall 41r. The liquid introduction channel 41 is formed with a peripheral wall 41k having a curvature.

[0066] Figure 6 Show Figure 4 A cross-sectional view of the swirl flow generating portion 42 taken along line IV-IV.

[0067] The swirling flow generating section 42 has a liquid introduction flow path 41 (see Figure 5 ) are connected to the two connection areas 42s. In addition, the swirl flow generating section 42 is capable of injecting the nozzle throttle hole 44 (refer to Figure 6 , Figure 4 ) as the center of the swirling flow to form a vortex shape.

[0068] The swirling flow 43 generated by the swirling flow generating unit 42 (see Figure 4 ) After passing through the injection nozzle throttle hole 44, it is sprayed from the injection nozzle outlet 45 to the buffer space 46 in the shell inner wall 4n.

[0069] The liquid injected into the buffer space 46 first forms an umbrella-shaped liquid film 47. Then, the front end of the liquid film 47 splits into liquid filaments 48, and then the liquid filaments 48 split to generate droplets 49 (spray 30) of fine droplets. In this way, the swirling flow 43 is formed in the liquid injection nozzle 31 (31a, 31b, 31c) (see Figure 4 ), it is possible to form atomized fine droplets 49 (spray 30) at a short distance from the liquid injection nozzle outlet 45.

[0070] <Directivity of Spray 30>

[0071] At once Figure 4 As for the liquid injection nozzle 31 shown in the figure, the central axis 31o of the injection nozzle 31 (31a, 31b, 31c) is inclined by θ relative to the swirl central axis 51 of the swirl flow generating portion 42 as a swirl chamber forming the swirl flow 43. When the inclination angle θ of the central axis 31o of the liquid injection nozzle 31 (31a, 31b, 31c) is adjusted, the umbrella-shaped liquid film 47 becomes an asymmetric shape, which can make the direction of the spray 30 directional. In this way, by adjusting the shape of the liquid injection nozzle 31 (31a, 31b, 31c), as shown in FIG. Figure 3 As shown, the injected spray 30 can be directed toward the low-pressure side of the compression chamber 13 .

[0072] Figure 7 A schematic cross-sectional view showing a mechanism by which the spray 30 has directivity.

[0073] The spray 30 has a directional property (refer to Figure 3 ) mechanism. Figure 7 In the figure, the outlet surface 31d of the injection nozzle 31 (31a, 31b, 31c) is not perpendicular to the central axis 31o of the liquid injection nozzle 31 (31a, 31b, 31c), but forms a height dimension 53 in the direction of the central axis 31o.

[0074] At the outlet of the liquid injection nozzle 31, the swirling flow 43 in the injection nozzle 31 is similarly formed until the swirling flow 54, but within the range of the height dimension 53, only Figure 7 The right side of the injection nozzle 31 (31a, 31b, 31c) forms a swirling flow 43. Figure 7 Compared with the left side, the swirling flow on the right side is strengthened, and thus the centrifugal force applied to the umbrella-shaped liquid film 47 is also increased. As a result, a Figure 7 The directional spray 30 on the right side.

[0075] <Liquid supply mechanism for enhancing the swirling flow 43 in the spray hole of the spray nozzle 31>

[0076] Figure 8 A schematic cross-sectional view showing liquid atomization in the liquid supply portion (injection nozzle 31) on the low-pressure side.

[0077] Fig. 9 A schematic cross-sectional view showing liquid atomization in a liquid supply portion (injection nozzle 31) on the high-pressure side.

[0078] use Figure 8 and Fig. 9 Explanation: From the low pressure side of the compression chamber 13 ( Figure 8 ) towards the high pressure side ( Fig. 9 ) to enhance the swirling flow 43 in the spray hole of the spray nozzle 31 (31a, 31b, 31c).

[0079] Figure 8 The structure for generating the swirling flow 43 on the low pressure side is shown. Fig. 9 The structure of the swirling flow 43 on the high pressure side is shown. Figure 8 In comparison, on the high-voltage side Fig. 9 In the structure, not only the diameter Φ of the injection nozzle throttle hole 44 is large, but also the size of the swirl flow generating portion 42 is large. By strengthening the swirl flow 43, the centrifugal force is strengthened, and the umbrella-shaped liquid film 47 can be thinned. Therefore, even if the diameter Φ of the injection nozzle is increased to maintain the liquid flow rate on the high-pressure side, the liquid atomization can be maintained by strengthening the centrifugal force.

[0080] <<Second Embodiment>>

[0081] exist Fig.10 China-Israel Figure 2 The view in the direction of I shows the liquid supply method according to the second embodiment of the present invention.

[0082] The liquid supply mechanism of the screw compressor 100A according to the second embodiment will be described.

[0083] The second embodiment is an example in which a liquid supply mechanism provided from the low-pressure side toward the high-pressure side of the compression chamber 13 is provided at an intermediate position between the male rotor 2 and the female rotor 3 .

[0084] The other configurations are the same as those of the first embodiment. The same components are denoted by the same reference numerals, and detailed descriptions thereof are omitted.

[0085] In the second embodiment, the spray 30 ejected from the liquid ejection nozzle 31A (31a1, 31b1, 31c1) is parallel to the compression side cusp 12 of the compression side intersection line and directed toward the low pressure side ( Fig.10 The spray 30 is supplied to the compression chamber 13. Therefore, the cooling and sealing properties of the compression chamber 13 can be improved by utilizing the liquid of the spray 30.

[0086] In addition, by making the spray 30 parallel to the compression side tip 12 of the compression side intersection line and toward the low pressure side ( Fig.10 on the upper side), the spray 30 can be evenly distributed to the male rotor 2 and the female rotor 3.

[0087] <<Third Embodiment>>

[0088] Fig.11 China-Israel Figure 2 The view in the direction of II shows the liquid supply method according to the third embodiment of the present invention.

[0089] The liquid supply mechanism of the screw compressor 100B according to the third embodiment will be described.

[0090] In the third embodiment, there is no Figure 3 The first embodiment shows that the liquid injection nozzles 31A (31a1, 31b1, 31c1) for injecting the spray 30 from the high pressure side to the low pressure side of the compression chamber 13 are arranged in a straight line. Fig.11 As shown, the liquid ejecting nozzles 31B (31a2, 31b2, 31c2) are arranged in a staggered manner or alternately.

[0091] By arranging the spray positions of the spray 30 in a staggered manner or at different positions from each other, it is possible to prevent the supply regions of the sprays 30 from overlapping, thereby supplying the spray 30 more uniformly over a wider range.

[0092] <<Fourth Embodiment>>

[0093] Fig.12 China-Israel Figure 2 The view in the direction of II shows the liquid supply method according to the third embodiment of the present invention.

[0094] The liquid supply mechanism of the screw compressor 100C according to the fourth embodiment will be described.

[0095] In the fourth embodiment, the directions of the sprays 30 ejected from the liquid ejection nozzles 31C (31a3, 31b3, 31c3) are arranged in a staggered or mutually different manner, based on the orthogonal directions of the ridgelines 26 of the male rotor 2 and the ridgelines 27 of the female rotor 3. The other configurations are the same as those of the first embodiment. The same reference numerals are given to the same components, and detailed descriptions are omitted.

[0096] By arranging the directions of the sprays 30 in a staggered manner or in different directions from each other, it is possible to prevent or suppress the supply areas of the sprays 30 from the liquid spray nozzles 31a3, 31b3, and 31c3 from overlapping, thereby supplying the sprays 30 more uniformly over a wider range.

[0097] <<Fifth Embodiment>>

[0098] Fig.13 by Figure 2 The view in the direction of II shows the liquid supply method according to the fifth embodiment of the present invention.

[0099] The liquid supply mechanism of the screw compressor 100D according to the fifth embodiment will be described.

[0100] In the fifth embodiment, the directions of the sprays 30 from the liquid supply mechanism provided from the low-pressure side toward the high-pressure side of the compression chamber 13 are arranged in a staggered manner or in a manner different from each other.

[0101] When the rotation speed of the screw rotor 1 is low, the inclined compression chamber 13 (see Figure 2 )’s shape effect becomes smaller.

[0102] Sometimes corresponding to the inclined compression chamber 13 (refer to Figure 2 ) shape and spraying in the direction from the low pressure area to the high pressure area.

[0103] according to Fig.13The spraying method shown can prevent or suppress the supply areas of the spray 30 sprayed from the liquid spray nozzles 31D (31a4, 31b4, 31c4) from overlapping, and can supply the spray more uniformly over a wider range.

[0104] By applying the above Figure 3 , Fig.10 , Fig.11 , Fig.12 , Fig.13 The combination can realize the supply of liquid (oil, etc.) more suitable for the operating state of the screw compressors 100 to 100D.

[0105] As described above, liquid supply suitable for the pressure change and shape change in the compression chamber 13 from the start to the end of compression can be achieved, and the compressed gas can be cooled and the gas leakage in the gaps between the parts can be reduced.

[0106] <<Other Implementation Methods>>

[0107] 1. The present invention is not limited to the configuration of the above-described embodiment, and various modifications and specific embodiments can be realized within the scope of the claims.

[0108] Description of Reference Numerals

[0109] 1 screw rotor

[0110] 2 positive rotor (screw rotor)

[0111] 3 female rotor (screw rotor)

[0112] 4 Shell

[0113] 13 Compression chamber (female side)

[0114] 19 Direction of movement of the ridgeline of the screw rotor

[0115] 26 Ridgeline of the male rotor (ridgeline)

[0116] 27 Ridgeline of the female rotor (ridgeline)

[0117] 30 sprays

[0118] 31 Liquid injection nozzle (liquid supply mechanism)

[0119] 31A, 31a1, 31b1, 31c1 are liquid injection nozzles (liquid supply means) facing in directions different from each other with respect to the advancing direction of the ridgeline of the screw rotor.

[0120] 31B, 31a2, 31b2, 31c2 Liquid injection nozzles (liquid supply means) facing in a direction perpendicular to the ridgeline of the screw rotor

[0121] 31C, 31a3, 31b3, 31c3 are liquid injection nozzles (liquid supply means) facing in different directions relative to the direction perpendicular to the ridgeline of the screw rotor.

[0122] 31D, 31a4, 31b4, 31c4 are liquid injection nozzles (liquid supply means) facing in different directions relative to the advancing direction of the ridgeline of the screw rotor.

[0123] 41 Liquid introduction flow path (liquid supply mechanism)

[0124] 42 Swirling flow generating unit (liquid supply mechanism)

[0125] 43 Swirling flow in the jet nozzle (swirling flow)

[0126] 44 Injection nozzle throttle hole (liquid supply mechanism)

[0127] 45 jet nozzle outlet

[0128] 47 Umbrella-shaped liquid film (liquid)

[0129] 48 Liquid Silk (Liquid)

[0130] 49 Fine droplets (liquid)

[0131] θ The inclination of the central axis of the liquid injection nozzle relative to the swirl central axis of the swirl chamber

[0132] 51 The central axis of the cyclotron chamber

[0133] Φ Nozzle diameter (diameter of the nozzle)

[0134] 54 Swirling flow at the outlet of the liquid injection nozzle (swirling flow)

[0135] 55 Swirling flow (swirling flow) with a height dimension 53 at the outlet of the liquid injection nozzle

[0136] 100, 100A, 100B, 100C, 100D screw compressors.

Claims

1. A screw compressor, characterized in that: include: Screw rotor; a housing for housing the screw rotor; as well as a liquid supply mechanism that supplies liquid from a liquid injection nozzle into a compression chamber formed by the screw rotor in the casing; The spray injected from the liquid injection nozzle is directed toward the low-pressure side of the compression chamber.

2. A screw compressor, characterized in that: include: Screw rotor; a housing for housing the screw rotor; as well as A plurality of liquid supply mechanisms supply liquid from liquid injection nozzles into compression chambers formed by the screw rotor in the casing, respectively. The liquid supply mechanism forms a swirling flow in the liquid injection nozzle. The liquid injection nozzle increases the diameter of a spray hole of the liquid injection nozzle from a low-pressure side to a high-pressure side of the compression chamber, and strengthens a swirling flow within the liquid injection nozzle.

3. The screw compressor according to claim 1, characterized in that: The liquid supply mechanism forms a swirling flow in the liquid ejecting nozzle.

4. The screw compressor according to claim 1 or 2, characterized in that: The spray injected from the liquid injection nozzle is directed in a direction perpendicular to a ridgeline of the screw rotor.

5. The screw compressor according to claim 1 or 2, characterized in that: The spray injected from the liquid injection nozzle is directed in directions different from each other with respect to a direction orthogonal to a ridgeline of the screw rotor.

6. The screw compressor according to claim 1 or 2, characterized in that: The spray injected from the liquid injection nozzle is directed in directions different from each other with respect to the advancing direction of the ridgeline of the screw rotor.

7. The screw compressor according to claim 2, characterized in that: The spray injected from the liquid injection nozzle is directed toward the low-pressure side of the compression chamber.

8. A screw compressor, characterized in that: include: Screw rotor; a housing for housing the screw rotor; as well as a liquid supply mechanism that supplies liquid from a liquid injection nozzle into a compression chamber formed by the screw rotor in the casing; The liquid supply mechanism directs the spray injected from the liquid injection nozzle toward the high-pressure side of the compression chamber and toward directions different from each other with respect to a traveling direction of a ridgeline of the screw rotor.

9. The screw compressor according to any one of claims 2, 3 and 7, characterized in that: The liquid supply mechanism is configured such that the central axis of the liquid jet nozzle is inclined relative to the swirl central axis of the swirl chamber forming the swirl flow.

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