阅读说明：本技术 空气压缩装置、马达的防尘方法 (Air compression device and dust prevention method of motor ) 是由 黑光将 田中源平 川畑庆太 久我崇 于 2020-02-12 设计创作，主要内容包括：本发明涉及空气压缩装置、马达的防尘方法。本发明是鉴于若空气压缩装置中粉尘向驱动压缩机的马达侵入则可能成为动作不良、故障的原因这样的课题而做成的,其一个目的在于提供一种能够降低粉尘向马达的侵入的空气压缩装置。空气压缩装置(100)包括：压缩机(10),其生成压缩空气；马达(12),其驱动压缩机(10)；以及空气导入部(26),其向马达(12)的内部导入压缩空气来提高该内部的压力。(The invention relates to an air compression device and a dust prevention method of a motor. The present invention has been made in view of the problem that dust may cause malfunction or failure when the dust enters a motor that drives a compressor in an air compressor, and an object thereof is to provide an air compressor capable of reducing the entry of dust into the motor. An air compression device (100) comprises: a compressor (10) that generates compressed air; a motor (12) that drives the compressor (10); and an air introduction unit (26) that introduces compressed air into the interior of the motor (12) to increase the pressure therein.)

1. An air compression device, wherein,

this air compression device includes:

a compressor that generates compressed air;

a motor that drives the compressor; and

and an air introduction unit that introduces the compressed air into the motor to increase the pressure therein.

2. The air compression device of claim 1,

the air introduction unit causes the inside of the motor to be at a positive pressure.

3. The air compressing device according to claim 1 or 2,

the motor has a rotating body and a stationary body,

a labyrinth is provided between the rotating body and the stationary body,

the compressed air inlet is provided on the opposite side of the labyrinth with the rotating body interposed therebetween.

4. The air compressing device according to any one of claims 1 to 3,

the air compression device further comprises:

a multi-wing fan that rotates integrally with the motor to generate an air flow; and

a cooler that cools the compressed air with the air flow,

the air introduction part is configured to introduce the compressed air cooled by the cooler into the motor,

the air compression device is provided under the floor of the railway vehicle.

5. A dust-proof method for a motor, wherein,

the dust-proof method of the motor comprises the following steps:

a step of generating compressed air by using a driving force of a motor; and

and a step of introducing the compressed air into the motor to increase the pressure in the motor.

6. The dust preventing method of a motor according to claim 5,

the method for preventing dust of a motor further includes a step of discharging air inside the motor from a gap between a rotating body and a stationary body of the motor.

7. The dust preventing method of a motor according to claim 5 or 6,

the dust-proof method of the motor further comprises the following steps:

a step of generating an air flow by a multi-wing fan that rotates integrally with the motor; and

a step of cooling the compressed air with the air flow,

the step of increasing the pressure includes a step of introducing the cooled compressed air into the motor.

Technical Field

The present invention relates to an air compressor device for generating compressed air and a dust-proof method for a motor.

Background

An air compressor device provided in a railway vehicle and generating compressed air used in the railway vehicle is known. For example, patent document 1 describes an air compression device including a compressor drive unit and a compressor, and coupling the compressor drive unit and the compressor via a coupling. In this air compression device, the compressor driving unit, the coupling housing, the cooling fan, and the aftercooler that cools the compressed air compressed by the compressor are housed in the housing case. The air compressor device further includes a mechanism for supplying oil to the compressor and a mechanism for recovering oil from compressed air compressed along with the oil.

Disclosure of Invention

Problems to be solved by the invention

The present inventors have studied an air compressor and have obtained the following findings.

A railway vehicle is equipped with an air compressor. Since the railway vehicle may run in an area where dust such as sand is large, it is necessary to take into consideration that the air compressor for the railway vehicle is not adversely affected by the dust. In this device, a motor is used to drive the compressor. The motor includes a rotor and a stator opposed to each other with a gap therebetween. If dust enters the gap, the dust interferes with the rotation of the motor, and may cause malfunction or failure.

A countermeasure for sealing the motor case is also conceivable, but in this case, components such as a seal are increased, which is disadvantageous in terms of cost and manufacturing. Further, a measure to reduce the gap between the rotating body and the housing is considered, but the processing and the assembly become difficult, and productivity and cost competitiveness are deteriorated. Such a problem may occur not only in an air compressor for a railway vehicle but also in other types of air compressors.

As described above, the present inventors have recognized that the air compression device described in patent document 1 has room for improvement in terms of reducing the intrusion of dust into the motor.

The present invention has been made in view of the above problems, and an object thereof is to provide an air compressor device capable of reducing the intrusion of dust into a motor.

Means for solving the problems

In order to solve the above problem, an air compressor according to an embodiment of the present invention includes: a compressor that generates compressed air; a motor driving the compressor; and an air introduction part which introduces compressed air into the motor to increase the pressure inside the motor.

According to this embodiment, the pressure inside the motor can be increased.

In addition, as an embodiment of the present invention, any combination of the above, and a mode in which the constituent elements, expressions, and the like of the present invention are replaced with each other in a method, an apparatus, a program, a temporary or non-temporary storage medium storing the program, a system, and the like are also effective.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the present invention, it is possible to provide an air compressor device capable of reducing the intrusion of dust into a motor.

Drawings

Fig. 1 is a system diagram schematically showing a configuration of an air compressor according to an embodiment of the present invention.

Fig. 2 is a schematic view showing a state in which the air compression device of fig. 1 is installed in a railway vehicle.

Fig. 3 is a front view schematically showing a compressor and a blower fan of the air compressing device of fig. 1.

Fig. 4 is another front view schematically showing a compressor and a blower fan of the air compressing device of fig. 1.

Fig. 5 is a view schematically showing the flow of air from the blower fan of the air compressor of fig. 1.

Fig. 6 is a side sectional view schematically showing the periphery of the compressor driving part and the sirocco fan of the air compressing apparatus of fig. 1.

Fig. 7 is a side sectional view showing an enlarged periphery of a labyrinth portion of the compressor driving portion of fig. 6.

Fig. 8 is a front view showing the periphery of a balance weight of the compressor driving unit of fig. 6.

Fig. 9 is a rear view showing the periphery of the balance weight of the compressor driving part of fig. 6.

Fig. 10 is a perspective view schematically showing a cooler of the air compressor of fig. 1.

Fig. 11 is a schematic view illustrating the flow of air of the cooler of fig. 10.

Fig. 12 is a front view schematically showing the periphery of a compressor of the air compression device according to modification 1.

Description of the reference numerals

10. A compressor; 12. a motor; 12c, a housing; 12n, a rotating body; 12p, a stationary body; 12r, maze; 14. a compressor driving part; 15. balancing the balance weight; 15b, a balance adjustment part; 16. a multi-wing fan; 18. the 1 st cooler; 20. a 2 nd cooler; 22. a cooler; 24. a dehumidifier; 26. an air introduction part; 26d, a valve mechanism; 28. a blower fan; 32. an air intake portion; 34. a compressed air delivery unit; 38. a bearing retainer; 40. an inverter control device; 42. a storage box; 90. a railway vehicle; 100. an air compression device.

Detailed Description

The present invention will be described below with reference to the drawings according to preferred embodiments. In the embodiment and the modifications, the same or equivalent constituent elements and members are denoted by the same reference numerals, and overlapping descriptions are appropriately omitted. In addition, the dimensions of the components in the drawings are shown enlarged or reduced as appropriate for easy understanding. In the drawings, some members that are not essential in describing the embodiments are omitted and shown.

In addition, although a term including ordinal numbers 1, 2, etc. is used to describe various components, the term is used only for the purpose of distinguishing one component from another component, and the components are not limited by the term.

[ embodiment 1 ]

The structure of an air compressor 100 according to embodiment 1 of the present invention will be described with reference to fig. 1 to 11. As an example, the air compressor 100 is provided under the floor of a railway vehicle, and can be used as an air compressor for supplying compressed air to the vehicle. Fig. 1 is a system diagram schematically showing the structure of an air compressor 100. Fig. 2 is a schematic view showing a state in which the air compressor 100 is installed in the railway vehicle 90. In the drawing, a part of the bearing holder 38 and a part of the multi-wing fan 16 are cut away for easy understanding, and the blower fan 28 is shown to be smaller than a real scale.

The air compressor 100 of the present embodiment includes a compressor 10, a compressor driving unit 14, a sirocco fan 16, a cooler 22, a dehumidifier 24, an air introducing unit 26, a blower fan 28, an air suction unit 32, a compressed air discharge unit 34, an inverter control device 40, and a housing case 36. The air compressor 100 compresses air taken in from the air intake unit 32 in the compressor 10, cools the air in the cooler 22, dehumidifies the air in the dehumidifier 24, sends the air out from the compressed air sending unit 34, and supplies the air to the vehicle 90.

Hereinafter, a direction along the center axis La of the rotary shaft 10a of the compressor 10 is referred to as an "axial direction", a circumferential direction of a circle centered on the center axis La is referred to as a "circumferential direction", and a radial direction of a circle centered on the center axis La is referred to as a "radial direction". For convenience, hereinafter, one side (right side in the drawing) in the axial direction is referred to as an input side, and the other side (left side in the drawing) is referred to as an opposite-to-input side. In this example, the motor 12 is provided on the input side of the compressor 10, and the compressor 10 is provided on the opposite side of the input of the motor 12.

The air intake portion 32 is provided in the housing case 36, and functions as a mechanism for taking in air (outside air) compressed by the compressor 10. The air intake portion 32 is formed to communicate with the compressor 10 via an intake pipe 32 b. The air intake unit 32 is provided with an intake filter 32a that suppresses the passage of dust such as sand dust when intake air passes through. The suction filter 32a may be a filter using mesh.

The compressed air delivery unit 34 functions as a mechanism for delivering compressed air Ar10d cooled by the cooler 22 and dehumidified by the dehumidifier 24, which will be described later. The compressed air delivery unit 34 supplies the generated compressed air Ar10d to the compressed air storage unit 92 provided outside the housing case 36.

The compressed air sending-out part 34 may include a valve mechanism 34d, and the valve mechanism 34d is provided in a path connecting the dehumidifier 24 and the compressed air storage part 92. The valve mechanism 34d may be a check valve that allows the compressed air Ar10d to pass toward the compressed air storage unit 92 when the pressure on the dehumidifier 24 side becomes equal to or higher than a predetermined pressure, and prevents a reverse flow from the compressed air storage unit 92.

The compressor 10 will be described with reference to fig. 2 and 3 to 5. These figures show the compressor 10 and the blower fan 28 as seen from arrow F of fig. 2. Fig. 3 is a front view schematically showing the compressor 10 and the blower fan 28. Fig. 4 shows a state where the fixed scroll portion 10j is removed. Fig. 5 shows the back space 10g with the orbiting scroll 10h removed. The compressor 10 of the present embodiment is a scroll-type air compressor including a rotary shaft 10a, a main body portion 10b, an intake port 10c, an exhaust port 10e, air cooling fins 10f, a orbiting scroll portion 10h, a fixed scroll portion 10j, and a back space 10 g.

The suction port 10c of the compressor 10 communicates with the air suction portion 32, and the compressor 10 compresses the air Ar32 sucked from the air suction portion 32 into the pump space 10d through the suction pipe 32 b. A valve mechanism 32d is provided between the air intake portion 32 and the intake port 10c of the compressor 10. The compressor 10 is operated to generate a negative pressure on the compressor 10 side, and the valve mechanism 32d is opened. The discharge port 10e communicates with the cooler 22, and the compressed air is discharged from the discharge port 10e to the cooler 22.

The body portion 10b is a circumferential outer peripheral wall defining the pump space 10 d. The main body portion 10b surrounds the fixed scroll 10m and the orbiting scroll 10n in the pump space 10 d. The fixed scroll portion 10j includes a fixed disk portion 10k having a plurality of air cooling fins 10f provided on the outer side thereof and a fixed scroll 10m fixed to the inner side of the fixed disk portion 10 k. A discharge port 10e is provided in the center of the fixed disk portion 10 k. The orbiting scroll portion 10h includes an orbiting disk portion 10p and an orbiting scroll 10n fixed to the orbiting disk portion 10 p. A rotary shaft 10a extending to the input side is fixed to the center of the rotating disk portion 10 p. A back space 10g is provided on the input side of the orbiting disk portion 10p, i.e., on the back side of the orbiting scroll portion 10 h. The cooling air is introduced from the blower fan 28 into the back space 10g to forcibly air-cool the rotary disk portion 10p and the rotary shaft 10 a. The blower fan 28 will be described later.

The orbiting scroll 10n and the fixed scroll 10m are scroll bodies of the same shape. The compressor 10 compresses air by changing the volume of a compression space by rotating the orbiting scroll 10n integrally with the rotary shaft 10a with respect to the fixed scroll 10 m. The compressor 10 sucks air from the outer periphery and performs a compression action toward the center. The compressor 10 may be an oil-free type compressor.

The blower fan 28 will be described with reference to fig. 2 and 3 to 5. The blower fan 28 is a blowing mechanism that sends air for cooling (hereinafter referred to as cooling air Ar28) to the compressor 10. The blower fan 28 supplies the cooling air Ar28 to the rear space 10g on the rear surface side of the orbiting scroll portion 10h to mainly cool the orbiting scroll portion 10 h.

The blower fan 28 of the present embodiment is an electric axial flow blower having a propeller 28 b. As shown in fig. 5, the blower fan 28 is disposed on the side of the compressor 10 such that the rotation axis L28 of the propeller 28b is perpendicular to the rotation shaft 10a of the compressor 10. An outside air filter 28a formed of a wire mesh or the like is provided on the upstream side of the blower fan 28. A blowing duct 28g for guiding the cooling air Ar28 to the center of the orbiting scroll portion 10h is provided downstream of the blower fan 28.

The blowing duct 28g has a substantially quadrangular frustum shape whose sectional area decreases as it approaches the compressor 10. The cooling air Ar28 is concentrated along the inner surface of the air blowing duct 28g, and intensively cools the central portion of the orbiting scroll portion 10 h. Since the center portion of the orbiting scroll portion 10h has the highest temperature, the cooling effect can be improved by cooling the portion with emphasis. An exhaust duct 28h is provided downstream of the rear space 10 g. In this example, the upstream side of the exhaust duct 28h faces the air blowing duct 28g, and the downstream side of the exhaust duct 28h faces downward.

The bearing holder 38 is explained with reference to fig. 2 and 6. Fig. 6 is a side sectional view schematically showing the periphery of the compressor driving unit 14 and the sirocco fan 16. The bearing holder 38 is provided on the input side of the compressor 10, and supports the bearings 38h and 38j, and the bearings 38h and 38j support the rotary shaft 10a so that the rotary shaft 10a can rotate. The bearing holder 38 has a hollow cylindrical portion 38a and a plurality of fins 38f extending radially outward from the cylindrical portion 38 a. The fin 38f has a triangular shape in which the radially outer end thereof extends radially outward as it approaches the compressor 10 in the axial direction. In this example, 4 fins 38f are provided at 90 ° intervals along the circumferential direction on the outer periphery of the cylindrical portion 38 a. The bearing holder 38 also has a function of dissipating heat generated in the compressor 10 to suppress excessive temperature rise of the bearings 38h, 38 j.

The bearings 38h and 38j include a 1 st bearing 38h disposed in the vicinity of the compressor 10 and a 2 nd bearing 38j disposed in the vicinity of the motor 12. The 1 st bearing 38h and the 2 nd bearing 38j support the rotary shaft 10a so that the rotary shaft 10a can rotate freely. The 1 st and 2 nd bearings 38h and 38j are held in the hollow portion of the cylindrical portion 38a so as to be spaced apart in the axial direction.

A part of the bearing holder 38 enters the inner peripheral portion of the sirocco fan 16 in the axial direction. At least a part of the bearing 38j supporting the rotary shaft 10a of the compressor 10 overlaps the sirocco fan 16 in the axial direction. In this case, the axial direction space can be effectively utilized as compared with the case where the overlapping is not performed.

The compressor driving unit 14 will be described with reference to fig. 2, 6, and 7. Fig. 7 is a side sectional view showing an enlarged periphery of the labyrinth portion 12f of the compressor driving portion 14. The compressor driving unit 14 mainly includes a motor 12 for driving and rotating the compressor 10 and a balance weight 15.

The motor 12 is explained. The motor 12 includes an output shaft 12a, a rotor 12k, a stator 12s, a housing 12c, and a labyrinth portion 12 f. In the present embodiment, the output shaft 12a of the motor 12 is provided integrally with the rotary shaft 10a of the compressor 10. The rotor 12k has a magnet 12m having a plurality of magnetic poles in the circumferential direction, and is fixed to the outer periphery of the output shaft 12 a.

The stator 12s includes a stator core 12j surrounding the rotor 12k with a magnetic gap therebetween, and a coil 12g wound around the stator core 12 j. The outer peripheral portion of the stator 12s is fixed to the inner peripheral surface of the housing 12 c. The housing 12c has a cylindrical portion 12d and a bottom portion 12e, and functions as an outer wall surrounding the rotor 12k and the stator 12 s. In this example, the case 12c has a bottomed cylindrical shape with the opposite input side open and the bottom portion 12e provided on the input side. The bottom portion 12e is provided with an inlet 12h for introducing air from the air inlet 26.

The labyrinth portion 12f is a member that closes the opposite side to the input side of the cylindrical portion 12d, and has a disk shape in this example. The labyrinth portion 12f includes a rotary body portion 12n fixed to the output shaft 12a and a stationary body portion 12p fixed to the cylindrical portion 12 d. In this example, the rotary body 12n has a disc shape, and the stationary body 12p has an annular shape. The rotary body 12n also serves as a balance weight 15 described later. A labyrinth 12r is provided between the rotary body 12n and the stationary body 12 p. In this example, the labyrinth 12r is a labyrinth in which curved gaps are combined. Since the labyrinth portion 12f includes the labyrinth 12r, the intrusion of dust into the motor 12 is reduced.

Further, since the compressed air Ar10e introduced from the inlet 12h flows outward from the labyrinth 12r, the dust in the labyrinth 12r is easily discharged outward by the flow.

The motor 12 supplies a drive current from the inverter control device 40 (drive circuit) to the coil 12g of the stator 12s, thereby generating an excitation magnetic field in the magnetic gap. The motor 12 generates a rotational driving force between the rotor 12k and the output shaft 12a by the action between the excitation magnetic field and the magnet 12m of the rotor 12 k. The rotational driving force of the output shaft 12a drives the compressor 10 via the rotary shaft 10 a. The bearing supporting the rotary shaft 10a is provided in the bearing holder 38 outside the compressor driving part 14, but not inside the compressor driving part 14.

Inverter control device 40 is described with reference to fig. 1 and 2. The inverter control device 40 functions as an inverter power supply device for driving and controlling the motor 12. By housing the inverter control device 40 in the housing box 42, the inverter control device 40 is prevented from coming into contact with dust or rainwater. The storage box 42 may be made of metal. The inverter control device 40 includes electronic components (neither shown) such as a switching power supply module and a smoothing capacitor for supplying a drive current to the coil 12 g.

Since these electronic components generate heat by themselves during operation, the temperature in the housing box 42 rises. If the temperature in the case rises, the life of these electronic components is shortened, which may cause a failure. In the present embodiment, the housing box 42 is provided on the path of the intake air Ar32 between the air intake portion 32 and the intake port 10c of the compressor 10. In this example, the storage box 42 is provided between the air intake portion 32 and the valve mechanism 32 d. That is, a part or all of the intake air Ar32 passes through the housing box 42 and is sent to the compressor 10 side. Since the intake air Ar32 passes through the housing box 42, the inside of the box is forcibly ventilated, and the electronic components of the inverter control device 40 are air-cooled. In this case, the temperature rise in the housing box 42 is suppressed, and the life of the electronic component is extended.

The balance weight 15 is also explained with reference to fig. 8 and 9. Fig. 8 is a front view showing the periphery of the balance weight 15. Fig. 9 is a rear view showing the periphery of the balance weight 15. In order to suppress the rotational vibration, it is considered to apply processing (hereinafter referred to as "balance adjustment") for individually reducing the unbalance amount of the rotational balance (dynamic balance) to the sirocco fan 16, the rotor 12k, and the like. In this case, the total amount of residual unbalance may become large due to the accumulation of the residual unbalance amount of each member after the balance adjustment, and there is a disadvantage in that the number of processing steps increases. Therefore, the present embodiment includes the balance weight 15 having the balance adjustment portion 15 b. The balance weight 15 of this example is a metal disk-shaped member, and as described above, also serves as the rotor 12n of the labyrinth 12f, and is fixed to the input side of the disk portion 16b of the sirocco fan 16.

The sirocco fan 16, the rotor 12k, the rotary shaft 10a, and the balance weight 15 are integrally configured, and in this state, balance adjustment for reducing the total amount of unbalance is applied to the balance weight 15. In the balance adjustment step, the multi-blade fan 16, the rotor 12k, the rotary shaft 10a, and the balance weight 15 are integrated to form a workpiece. The workpiece is rotated in the balance check device to determine the amount and location of the imbalance. The balance adjustment portion 15b of the balance weight 15 is added or reduced in mass according to the determination result of the inspection device. The balance adjustment portion 15b on one side or both sides of the balance weight 15 can be added or reduced in mass. As shown in fig. 8 and 9, the balance adjustment portion 15b is a flat annular portion in the radial middle region of the balance weight 15.

The multi-blade fan 16 is explained with reference to fig. 6 and 7. The sirocco fan 16 functions as a blower that intensively discharges the air flow generated from the center portion toward the outer peripheral portion thereof to the discharge duct 16 d. The multi-bladed fan 16 is sometimes referred to as a sirocco fan. The sirocco fan 16 includes a disk portion 16b, a plurality of blades 16c, a casing 16e, and a delivery duct 16 d.

The disk portion 16b is a hollow disk-shaped member fixed to the rotation shaft 10a at the center. The plurality of blades 16c are positioned near the outer periphery of the disk portion 16b and extend from the disk portion 16b toward the opposite input side. The plurality of blades 16c are arranged at predetermined angular intervals in the circumferential direction. The casing 16e is a cylindrical member surrounding the disk portion 16b and the plurality of blades 16 c.

As shown in fig. 7, the disk portion 16b is disposed on the opposite side to the input side of the motor 12 with an axial gap 16g therebetween. The width W16 of the axial gap 16g may be narrower than the thickness H16 of the disc portion 16 b. In the axial direction, the blade 16c overlaps the 2 nd bearing 38j in the axial direction.

The delivery duct 16d is a tubular member extending from the casing 16e to the cooler 22. The lower portion 16h of the delivery duct 16d is a substantially square tubular portion extending upward from the upper portion of the housing 16 e. The upper portion 16j of the delivery duct 16d communicates with the lower portion of the cooler 22 from the upper portion of the lower portion 16 h. The upper portion 16j has a substantially rectangular truncated pyramid shape with a wide upper side.

The sirocco fan 16 may be overlapped with at least a part of the bearing 38j supporting the rotary shaft 10a of the compressor 10 in the axial direction. In this case, the axial length of the air compressor 100 can be shortened as compared with a case where the sirocco fan 16 does not overlap the bearing 38 j.

The cooler 22 will be described with reference to fig. 2, 6, 10, and 11. The cooler 22 cools the high-temperature (e.g., 200 to 250 ℃) compressed air supplied from the compressor 10 to a temperature slightly higher than room temperature (e.g., 40 to 50 ℃) and supplies the cooled air to the dehumidifier 24. The cooler 22 may be constituted by a single cooler, but in the present embodiment, a plurality of coolers are connected in series. The cooler 22 of the present embodiment includes a 1 st cooler 18 that primarily cools the compressed air from the compressor 10, and a 2 nd cooler 20 that secondarily cools the compressed air cooled by the 1 st cooler 18.

The 1 st cooler 18 and the 2 nd cooler 20 have bent pipes 18p and 20p and pipe receiving portions 18c and 20c that receive the pipes, respectively. The bent pipes 18p and 20p have a plurality of bent portions in a meandering manner, and flow compressed air from one end of the pipe to the other end. The pipe housing portions 18c and 20c have vertically thin outer walls in the shape of square cylinders, and function as wind tunnels for vertically flowing cooling air flows.

Wire mesh sections 18m, 20m for supporting the bent tubes 18p, 20p are fixed to the lower portions of the tube housing sections 18c, 20 c. The upper surface of the tube housing portion 20c is open, and the wire mesh portion 18n is fixed to the upper surface of the tube housing portion 18 c. Thus, the tube housing portions 18c and 20c have a structure in which the air flow easily passes vertically.

The 1 st introduction portion 18b provided at one end of the bent tube 18p protrudes outward from the side wall of the tube housing portion 18c of the 1 st cooler 18. The 1 st introduction portion 18b communicates with the discharge port 10e of the compressor 10. The 1 st lead-out portion 18e provided at the other end of the bent tube 18p protrudes outward from the side wall of the tube housing portion 18c of the 1 st cooler 18. The 1 st lead-out portion 18e communicates with the 2 nd lead-in portion 20 b.

The 2 nd introduction portion 20b provided at one end of the bent tube 20p protrudes outward from the bottom of the tube housing portion 20c of the 2 nd cooler 20. The 2 nd introduction portion 20b communicates with the 1 st lead-out portion 18 e. The 2 nd lead-out portion 20e provided at the other end of the bent tube 20p protrudes outward from the side wall of the tube housing portion 20c of the 2 nd cooler 20. The 2 nd lead-out portion 20e communicates with the dehumidifier 24.

The tube housing portion 18c is disposed above the tube housing portion 20 c. The air flow Ar16a sent from the sirocco fan 16 is supplied to the lower surface of the tube housing portion 20c via the duct 16 d. The air flow Ar16a flows through the gap between the wire mesh part 20m and the gap between the bent tubes 20p, and is discharged from the upper surface of the tube housing part 20 c. The compressed air of the bent pipe 20p is cooled by passing the air flow Ar16a through the outer peripheral surface of the bent pipe 20 p.

The air flow Ar16b discharged from the tube housing portion 20c is supplied to the lower surface of the tube housing portion 18 c. The air flow Ar16b flows through the gaps of the wire mesh parts 18m, the gaps of the bent tubes 18p, and the gaps of the wire mesh parts 18n, and is discharged from the upper surface of the tube accommodating part 18 c. By passing the air flow Ar16b through the outer peripheral surface of the bent tube 18p, the compressed air Ar20c of the bent tube 18p is cooled. The air discharged from the pipe housing portion 18c diffuses into the atmosphere.

In this way, the air flow Ar16a sent from the sirocco fan 16 is first supplied to the 2 nd cooler 20 and is used for secondary cooling of the primarily cooled compressed air. The air flow Ar16b discharged from the 2 nd cooler 20 is supplied to the 1 st cooler 18 and used for primary cooling of the compressed air. Compared to the case where the air flow Ar16a is first used for the primary cooling, the temperature difference between the compressed air and the cooling air in the secondary cooling becomes large, and thus the cooling efficiency can be improved.

The cooler 22 may be disposed at any position as long as a desired cooling effect can be obtained. The cooler 22 of the present embodiment is disposed above the center in the vertical direction of the air compression device 100. In particular, the cooler 22 is disposed between the sirocco fan 16 and the floor of the railway vehicle 90. By shortening the path of the air flow Ar16a sent from the sirocco fan 16, an extra piping space is eliminated. Further, the front-rear length of the air compressor 100 can be shortened as compared with the case where the multi-blade fan 16 is disposed in the front-rear direction.

The dehumidifier 24 is provided in a path that communicates the cooler 22 with the compressed air sending unit 34. The dehumidifier 24 is a hollow fiber membrane type dehumidifying device that dehumidifies the cooled compressed air Ar10 c. The dehumidifier 24 may comprise a filter element containing a desiccant. In the dehumidifier 24, final dehumidification of the compressed air Ar10d sent out from the compressed air sending unit 34 is performed. The compressed air Ar10d is sent to the compressed air storage unit 92 through the compressed air sending unit 34.

The air inlet 26 introduces the compressed air Ar10d dehumidified by the dehumidifier 24 into the casing 12c of the motor 12. By introducing the compressed air Ar10d, the pressure inside the casing 12c can be made positive higher than the external air pressure, and the intrusion of dust can be reduced. The air inlet 26 sends the compressed air Ar10d to the inlet 12h provided in the bottom 12 e. The air inlet 26 is provided with a valve mechanism 26d on a path for introducing the compressed air Ar10d from the dehumidifier 24 to the casing 12 c. The valve mechanism 26d may be a check valve that allows the compressed air Ar10d to pass through to the casing 12c side when the pressure in the dehumidifier 24 side becomes equal to or higher than a predetermined pressure, and blocks the reverse flow from the casing 12c to the dehumidifier 24.

The housing case 36 houses the compressor 10, the compressor driving unit 14, the sirocco fan 16, the cooler 22, the dehumidifier 24, the air introducing unit 26, the blower fan 28, the air suction unit 32, the compressed air sending unit 34, and the housing box 42 of the inverter control device 40.

An outline of an embodiment of the present invention is as follows. An air compressor 100 according to an embodiment of the present invention includes: a compressor 10 that generates compressed air; a motor 12 that drives the compressor 10; and an air introduction portion 26 that introduces compressed air into the interior of the motor 12 to increase the pressure therein.

According to this embodiment, the pressure inside the motor 12 can be increased to reduce the intrusion of dust into the inside.

In the air compression device 100, the air introduction portion 26 may be configured to make the inside of the motor 12 positive pressure. In this case, the flow of air from the inside to the outside of the motor 12 can be formed to facilitate the discharge of the dust to the outside.

In the air compressor 100, the motor 12 may have a rotating body 12n and a stationary body 12p, a labyrinth 12r may be provided between the rotating body 12n and the stationary body 12p, and the compressed air inlet may be provided on the opposite side of the labyrinth 12r with the rotating body 12n interposed therebetween. In this case, the airflow from the labyrinth 12r to the outside is easily formed, and the dust adhering to the labyrinth 12r can be discharged from the labyrinth 12 r.

The air compressing apparatus 100 may further include: a multi-wing fan 16 that rotates integrally with the motor 12 to generate an air flow; and a cooler 22 that cools the compressed air with an air flow. The air introduction portion 26 may be configured to introduce the compressed air cooled by the cooler 22 into the motor 12. The air compressor 100 may be provided under the floor of the railway vehicle. In this case, since multi-blade fan 16 can be rotated by the rotation of motor 12, it is not necessary to provide a separate motor for generating an air flow. In addition, compared to the structure in which the compressed air before cooling is introduced, the temperature rise of the motor 12 can be suppressed.

[ 2 nd embodiment ]

Embodiment 2 of the present invention is a method for preventing dust in a motor. The dustproof method comprises the following steps: a step of generating compressed air by using the driving force of the motor 12; and a step of introducing compressed air into the interior of the motor 12 to increase the pressure of the interior. According to this embodiment, the pressure inside the motor 12 can be increased to reduce the intrusion of dust into the inside.

The above-described dust-proofing method may further include a step of discharging air inside the motor 12 from a gap between the rotating body 12n and the stationary body 12p of the motor 12. In this case, the discharge of the dust to the outside can be promoted by forming an air flow from the inside of the motor 12 to the outside through the gap.

In the above-described dust-proof method, the gap between the rotary body 12n and the stationary body 12p may be a labyrinth 12r formed between the rotary body 12n and the stationary body 12 p. In this case, the dust adhering to the labyrinth 12r can be discharged from the labyrinth 12 r.

The above-mentioned dust-proof method may further include: a step of generating an air flow by a sirocco fan 16 rotating integrally with the motor 12; and a step of cooling the compressed air by the air flow, wherein the step of increasing the pressure includes a step of introducing the cooled compressed air into the motor 12. In this case, since multi-blade fan 16 can be rotated by the rotation of motor 12, it is not necessary to provide a separate motor for generating an air flow. In addition, compared to the structure in which the compressed air before cooling is introduced, the temperature rise of the motor 12 can be suppressed.

[ embodiment 3 ]

Embodiment 3 of the present invention is an air compressor. The air compression device 100 includes a motor 12 that drives a compressor 10 for generating compressed air, and the inside of the motor 12 is set to a positive pressure. In order to make the inside of the motor 12 positive, the compressed air generated by the compressor 10 may be introduced into the casing 12c of the motor 12 by the air introduction portion 26, or air sent from another air generating device may be introduced into the casing 12 c.

With this configuration, the interior of the housing 12c of the motor 12 can be made positive in pressure, thereby reducing the intrusion of dust.

The embodiments of the present invention have been described in detail. The above embodiments are merely specific examples for carrying out the present invention. The contents of the embodiments do not limit the technical scope of the present invention, and a large number of design changes such as changes, additions, and reductions of the components can be made without departing from the spirit of the invention defined in the claims. In the above-described embodiments, the description is given by adding expressions such as "in the embodiments" and "in the embodiments" to the contents that can be subjected to such design change, but it is not allowable to subject the contents that are not subjected to such expressions to design change.

[ modified examples ]

Hereinafter, modifications will be described. In the drawings and the description of the modified examples, the same or equivalent constituent elements and members as those of the embodiment are denoted by the same reference numerals. The description overlapping with the embodiment is appropriately omitted, and the description will focus on the structure different from that of embodiment 1.

[ 1 st modification ]

An air compressor device 200 according to modification 1 will be described with reference to fig. 12. The present modification differs from the embodiment in that the supercharger 210 is provided at the suction port of the compressor 10, and the other configurations are the same, so the description focuses on the supercharger 210. Fig. 12 is a front view showing the periphery of the compressor 10, and corresponds to fig. 3.

In the scroll compressor, since the outer peripheral portion becomes a negative pressure, dust is easily sucked by a pressure difference between the outside and the inside. In order to reduce the intrusion of dust, the compressor 10 is provided with a surface seal (not shown) for sealing the outer peripheral surface. However, the surface seal has a gap called a seam, and dust enters from the gap. Therefore, in the present modification, the supercharger 210 is provided at the suction port 10c of the compressor 10.

The supercharger 210 is not particularly limited as long as it can increase the internal pressure of the compressor 10. The supercharger 210 of the present modification includes an impeller 210b rotated by a motor 210 m. The supercharger 210 pressurizes upstream air to make the downstream air to be at atmospheric pressure or higher, and supplies the pressurized downstream air to the suction port 10c of the compressor 10. The supercharger 210 is provided on a path between the valve mechanism 32d and the intake port 10 c. By providing the supercharger 210, the internal pressure in the vicinity of the suction port 10c of the compressor 10, that is, in the outer peripheral portion of the compressor 10 is increased, and the intrusion of dust due to negative pressure can be suppressed.

[ other modifications ]

In the description of the embodiment, the output shaft 12a of the motor 12 is integrated with the rotary shaft 10a of the compressor 10, but the present invention is not limited thereto. For example, the output shaft of the motor and the rotary shaft of the compressor may be separate bodies and coupled by a coupling or the like.

In the description of the embodiment, the valve mechanism 26d is an example of a check valve, but the present invention is not limited to this. For example, the valve mechanism 26d may be a secondary pressure regulating valve (pressure reducing valve) capable of adjusting the secondary side pressure.

In the description of the embodiment, the motor 12 is a surface magnet type DC brushless motor, but the present invention is not limited thereto. The motor may be any motor as long as it can drive the compressor, and may be any other type of motor such as a magnet embedded motor, an AC motor, a brush motor, and a gear motor.

In the description of the embodiment, the motor 12 is described as an example in which the stator and the rotor are separately incorporated in the compressor without including a bearing, but the present invention is not limited to this. For example, the motor may have a non-built-in structure in which a bearing, a rotor, and a stator are integrated in a motor case.

In the description of the embodiment, the rotating body 12n of the labyrinth 12f is also used as the balance weight 15, but the present invention is not limited thereto. The rotating body portion of the labyrinth portion may be provided independently of the balance weight.

In the description of the embodiment, the compressor 10 is of a scroll type, but the present invention is not limited thereto. The compressor may be any type of compressor as long as it can generate compressed air, and may be, for example, a screw type or reciprocating type air compressor.

The modification described above exerts the same actions and effects as those of embodiment 1.

In addition, any combination of the above-described embodiment and the modification is also useful as an embodiment of the present invention. The new embodiment resulting from the combination has the respective effects of the combined embodiment and the modified example at the same time.