CN111550410A

CN111550410A - Air compressor

Info

Publication number: CN111550410A
Application number: CN202010088782.4A
Authority: CN
Inventors: 黑光将; 久我崇; 川畑庆太; 田中源平
Original assignee: Nabtesco Corp
Current assignee: Nabtesco Corp
Priority date: 2019-02-12
Filing date: 2020-02-12
Publication date: 2020-08-18
Also published as: EP3696409A1; JP7388817B2; JP2020133404A

Abstract

The invention provides an air compression device. The present invention has been made in view of the problems associated with cooling of a supply device, and an object thereof is to provide an air compressor device capable of efficiently cooling a supply device that supplies electric power to a motor. An air compression device (100) comprises: a compressor that compresses air drawn from the suction path and sends the compressed air to the sending path; a motor driving the compressor; a supply device that supplies drive power to the motor; and a cooling unit (42) that is provided in at least a part of the suction path or at least a part of the delivery path to cool the supply device.

Description

Air compressor

Technical Field

The present invention relates to an air compressor.

Background

Air compressors that generate compressed air are known. For example, patent document 1 describes a hermetic compressor having a compressor main body driven by an electric motor. The compressor includes: a compressor main body that compresses air; a motor driving the compressor main body; an inverter that controls a rotation speed of the motor; and a cooling fan provided in the compressor main body. The inverter is provided in an intake path of cooling air generated by the cooling fan.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2016-075159

Disclosure of Invention

Problems to be solved by the invention

The present inventors have obtained the following knowledge about an air compression device.

Electronic components such as a switching power supply and a smoothing capacitor, which constitute a supply device for supplying electric power to a motor, such as an inverter, generate heat by themselves during operation. In order to suppress the temperature rise of the electronic component, it is desirable to cool the supply device. In the compressor described in patent document 1, the inverter is disposed in the duct, and air sucked from the suction port of the casing by the cooling fan provided in the compressor main body is passed through the duct, thereby cooling the inverter. In order to reduce the size and the like, the compressor described in patent document 1 cannot be said to sufficiently fulfill this requirement, though the cooling supply device is required to be efficiently cooled.

The present inventors have thus recognized that there is room for improvement in the air compressor from the viewpoint of efficiently cooling the supply device.

The present invention has been made in view of the above problems, and an object thereof is to provide an air compressor capable of efficiently cooling a supply device that supplies electric power to 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 compresses air drawn from the suction path and sends the compressed air to the sending path; a motor driving the compressor; a supply device that supplies drive power to the motor; and a cooling unit provided in at least a part of the suction path or at least a part of the delivery path to cool the supply device.

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 capable of efficiently cooling a supply device that supplies electric power to a motor.

Drawings

Fig. 1 is a system diagram schematically showing the configuration of an air compressor according to embodiment 1 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 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. 4 is a side sectional view showing an enlarged periphery of a labyrinth portion of the compressor driving portion of fig. 3.

Fig. 5 is a perspective view showing the periphery of an inverter control device of the air compressor apparatus of fig. 1.

Fig. 6 is a front view illustrating a balance weight and a sirocco fan of the compressor driving part of fig. 3.

Fig. 7 is a rear view illustrating a balance weight and a sirocco fan of the compressor driving part of fig. 3.

Fig. 8 is a front view schematically showing a compressor and a blower fan of the air compressing device of fig. 1.

Fig. 9 is another front view schematically showing a compressor and a blower fan of the air compressing device of fig. 1.

Fig. 10 is a view schematically showing the flow of air from the blower fan of fig. 8.

Fig. 11 is a perspective view schematically showing a cooler of the air compressor of fig. 1.

Fig. 12 is a schematic view illustrating the flow of air of the cooler of fig. 11.

Fig. 13 is a system diagram schematically showing the configuration of an air compressor according to embodiment 2 of the present invention.

Fig. 14 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 cooling section; 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 the drawings. 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 a railway vehicle that supplies 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.

The compressor driving unit 14 drives the compressor 10. The inverter control device 40 drives the motor 12 of the compressor drive unit 14. Multi-wing fan 16 is driven by motor 12 to generate an air flow for cooling in cooler 22. The air introduction portion 26 introduces compressed air into the motor 12, and the blower fan 28 generates an air flow for cooling the compressor 10.

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 driving unit 14 will be described with reference to fig. 2, 3, and 4. Fig. 3 is a side sectional view schematically showing the periphery of the compressor drive unit 14 and the sirocco fan 16. Fig. 4 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 rotor 12k is fixed to an input side of a rotor fixing portion 15d of a balance weight 15 (described later) by a fastener such as a bolt (not shown). These fastenings may be combined with an adhesive.

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 provided to cover 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. The stationary body portion 12p is an annular disk member having a stationary body side labyrinth forming portion 12q provided on the outer peripheral portion of the input opposite side end surface. The stationary body side labyrinth forming portion 12q has a stationary body side concave portion 12t and a stationary body side convex portion 12 u. The stationary body side concave portion 12t is entered by a labyrinth convex portion 15h described later. The stationary body side convex portion 12u enters a labyrinth concave portion 15g described later. The stationary body side convex portion 12u is an annular wall provided on the inner peripheral side of the stationary body side concave portion 12 t. 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 an inverter control device 40 (drive circuit) described later 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 sirocco fan 16 and 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.

Cooling unit 42 and inverter control device 40 will be described with reference to fig. 1, 2, and 5. Fig. 5 is a perspective view showing the periphery of inverter control device 40. For the interior to be visible, the figure is shown with the upper plate removed and a partial cut-away of the opposite wall 42 b. As shown in fig. 5, the cooling unit 42 of the present embodiment functions as a storage box that stores the inverter control device 40. By housing inverter control device 40 in cooling unit 42, inverter control device 40 is prevented from coming into contact with dust or rainwater. The cooling unit 42 of the present embodiment is a metal box having six closed surfaces in the shape of a rectangular parallelepiped, and has opposing

walls

42b and 42d that face each other.

As shown in fig. 1 and 2, the cooling unit 42 is provided in an intake path of the intake air Ar32, and introduces the intake air Ar32 from the intake path. In particular, cooling unit 42 is provided on a path between air intake unit 32 and suction port 10c of compressor 10. That is, a filter 32a that suppresses the passage of dust is provided upstream of the cooling unit 42. Further, a valve mechanism 32d (check valve) that allows air to flow into the compressor 10 is provided downstream of the cooling portion 42.

The inverter control device 40 functions as a supply device that supplies electric power for driving the motor 12 that drives the compressor 10. As shown in fig. 5, inverter control device 40 includes electronic component 40p, printed circuit board 40b, and heat sink 40 h. The electronic component 40p is a switching power supply module, a smoothing capacitor, or the like that supplies a drive current to the coil 12g of the motor 12. The printed circuit board 40b realizes a predetermined electronic circuit by electrically connecting the electronic components 40p and supports the electronic components 40 p.

Since the electronic component 40p generates heat by itself during operation, the temperature in the cooling portion 42 rises. When the temperature in the case rises, the internal temperature of the electronic component 40p rises due to self-heating, and the life is shortened, which causes a failure. Therefore, inverter control device 40 has heat sink 40h that cools electronic component 40 p. The radiator 40h may be disposed at least partially in the suction path or at least partially in the discharge path.

The heat sink 40h is not limited to the heat sink 40h, but the heat sink 40h of this example includes a flat plate-like base portion 40e attached to the printed circuit board 40b, and a plurality of fins 40f protruding from the base portion 40e to the side opposite to the printed circuit board 40 b. Heat generated by the electronic component 40p is transferred to the base 40e and the plurality of fins 40f via the circuit board 40 b.

The cooling unit 42 is provided with an inlet 42p for introducing the intake air Ar32 and an outlet 42s for discharging the intake air Ar 32. The intake air Ar32 is introduced from the inlet 42p and discharged from the outlet 42s, whereby the cooling portion 42 is forcibly ventilated, the temperature rise in the cooling portion 42 is suppressed, and the internal temperature of the electronic component 40p is decreased.

The intake air Ar32 introduced into the cooling portion 42 forms an air flow flowing from the inlet portion 42p to the outlet portion 42 s. It is desirable that the flow path resistance of the air flow be small. Therefore, in the present embodiment, the inlet portion 42p is provided on one opposing wall 42b, and the outlet portion 42s is provided on the other opposing wall 42 d. In particular, the inlet 42p and the outlet 42s are disposed at positions facing each other so that the distance therebetween is minimized. In the example of fig. 5, the inlet portion 42p and the outlet portion 42s are disposed at the centers in the width direction of the opposing

walls

42b, 42 d.

In order to promote heat dissipation of the heat sink 40h, it is desirable that the air flow passes over the surfaces of the base 40e and the fins 40 f. In the present embodiment, the radiator 40h is disposed in the flow path of the air flow in the cooling unit 42. In particular, the heat sink 40h is disposed such that the heat radiation surface 42m thereof is in contact with the air flow in the housing box. In the example of fig. 5, the base 40e and the fins 40f extend in the direction of the air flow of the cooling portion 42, and are arranged so as not to obstruct the air flow. Specifically, the base portion 40e and the heat radiation surfaces 42m of the fins 40f are set substantially parallel to a line connecting the inlet portion 42p and the outlet portion 42s so as to follow the air flow. In particular, the two fins 42f are disposed so as to sandwich a line connecting the inlet portion 42p and the outlet portion 42s, and a main flow (a major large flow) of the air flow is sandwiched between the two fins 42f so as to pass between the two fins 42 f.

The multi-blade fan 16 will be described with reference to fig. 3, 4, 6, and 7. Fig. 6 is a front view showing the sirocco fan 16 fixed to the balance weight 15. Fig. 7 is a rear view showing the sirocco fan 16 fixed to the balance weight 15. The sirocco fan 16 is disposed between the compressor 10 and the motor 12 in the axial direction. The sirocco fan 16 functions as a fan that rotates integrally with the rotor 12k of the motor 12. In particular, 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 and a plurality of blades 16 c.

The disk portion 16b is an annular disk member whose inner circumferential side is fixed to the rotary shaft 10a via a balance weight 15. In particular, the disk portion 16b is fixed to a fan fixing portion 15c provided on an end surface on the opposite side to the input side of the balance weight 15 by a fastener such as a bolt (not shown). These fastenings may be combined with an adhesive. 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 plurality of blades 16c function as an airflow generating portion that generates an airflow toward the outer peripheral portion by rotating. The casing 16e is a cylindrical member surrounding the disk portion 16b and the plurality of blades 16 c.

As shown in fig. 4, the disc portion 16b is disposed on the end surface 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. As shown in fig. 3, 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 balance weight 15 is explained with reference to fig. 6 and 7. The balance weight 15 also functions as an intermediate member disposed between the rotor 12k and the sirocco fan 16. The balance weight 15 is a disk-shaped member made of metal such as brass, and also serves as the rotating body 12n of the labyrinth 12f as described above. The balance weight 15 includes

balance adjusting portions

15a and 15b, a fan fixing portion 15c, a rotor fixing portion 15d, a shaft fastening portion 15f, and a labyrinth forming portion 15 e.

The fan fixing portion 15c is an annular portion to which the sirocco fan 16 is fixed on the end surface on the opposite side to the input side. The rotor fixing portion 15d is an annular portion for fixing the rotor 12k to the input-side end surface, and in this example, the rotor fixing portion 15d has a cylindrical outer shape protruding from the outer peripheral portion toward the input side. The shaft fastening portion 15f is a through hole through which the output shaft 12a is inserted and fixed to the output shaft 12 a.

The labyrinth forming portion 15e is a portion in which a labyrinth concave portion 15g and a labyrinth convex portion 15h are provided on the outer peripheral portion of the input-side end surface. The labyrinth recess 15g is an annular recess formed on the labyrinth forming portion 15e on the opposite side to the input side. The stationary body side convex portion 12u enters the labyrinth concave portion 15g through a gap. The labyrinth projection 15h is a portion that enters the stationary body side concave portion 12t with a gap therebetween. The labyrinth projection 15h in this example is an annular wall provided so as to surround the outer peripheral side of the labyrinth recess 15 g.

The

balance adjusting portions

15a and 15b are portions to which processing is applied to reduce the total unbalance amount of the balance weight 15, the rotor 12k, and the sirocco fan 16. That is, balance adjustment for reducing the total amount of unbalance of the balance weight 15, the rotor 12k, and the sirocco fan 16 is performed to the

balance adjustment portions

15a and 15b in a state where the sirocco fan 16 and the rotor 12k are fixed to the balance weight 15 and integrated with the balance weight 15.

The

balance adjustment portions

15a and 15b may be provided only on one end surface of the balance weight 15, but are provided on both end surfaces in the present embodiment. The

balance adjusting portions

15a and 15b include a fan-side adjusting portion 15a located radially inward of the fan fixing portion 15c and a rotor-side adjusting portion 15b located radially outward of the rotor fixing portion 15 d. In particular, the balance adjustment portion 15a may be provided radially inward of the airflow generation portion of the sirocco fan 16. In this example, the balance adjustment portion 15a is provided radially inward of the plurality of blades 16 c. As shown in fig. 6 and 7, the

balance adjustment portions

15a and 15b of this example are flat annular portions in the radial middle region of the balance weight 15.

The compressor 10 will be described with reference to fig. 2 and 8 to 10. These drawings show the compressor 10 and the blower fan 28 as viewed from an arrow F of fig. 2. Fig. 8 is a front view schematically showing the compressor 10 and the blower fan 28. Fig. 9 shows a state where the fixed scroll portion 10j is removed. Fig. 10 shows a 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, 8 to 10. 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. 10, 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 throttled along the inner surface of the air blowing duct 28g, and intensively cools the center 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 cooler 22 will be described with reference to fig. 2, 3, 11, and 12. 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 bearing holder 38 is explained with reference to fig. 2 and 3. 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 housing case 36 houses the compressor 10, the compressor drive unit 14, the sirocco fan 16, the cooler 22, the dehumidifier 24, the air introduction unit 26, the blower fan 28, the air intake unit 32, the compressed air delivery unit 34, and the cooling unit 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 that compresses air drawn from the suction path and sends the compressed air to the sending path; a motor driving the compressor; a supply device that supplies drive power to the motor; and a cooling unit 42 provided in at least a part of the suction path or at least a part of the delivery path to cool the supply device.

According to this embodiment, the interior of the cooling portion 42 is forcibly ventilated by the introduced air, and the temperature rise of the inverter control device 40 is suppressed, thereby extending the life of the electronic component 40 p. Since the inside of the cooling unit 42 is forcibly ventilated, it is not necessary to provide a space in the box with a margin, and the cooling unit 42 can be downsized.

Inverter control device 40 may have radiator 40h disposed at least in part of the intake path or at least in part of the delivery path. In this case, the radiator is efficiently cooled by the introduced air, and the temperature rise of the inverter control device 40 can be further suppressed.

The cooling unit 42 may be provided in the suction path, and a filter for suppressing passage of dust may be provided upstream of the cooling unit 42. In this case, the amount of dust entering the cooling portion 42 can be reduced.

A check valve may be provided that allows the flow of air from the cooling portion 42 to the compressor 10 and prevents the flow of air from the compressor 10 to the cooling portion 42. In this case, the backflow from compressor 10 to cooling unit 42 can be prevented.

The air compressor 100 may be a railway vehicle air compressor disposed under the floor of the railway vehicle 90. In this case, compressed air can be supplied to the railway vehicle 90. Further, since the inside of the cooling unit 42 is forcibly ventilated, it is not necessary to leave a space in the box empty, and the cooling unit 42 can be downsized. Therefore, the vehicle can be easily disposed in the underfloor space of the railway vehicle 90, and the underfloor space can be made vacant.

The above is the description of embodiment 1.

[ 2 nd embodiment ]

An air compressor 100 according to embodiment 2 of the present invention will be described with reference to fig. 13. Fig. 13 is a system diagram schematically showing the configuration of the air compressor apparatus 100 according to embodiment 2, and corresponds to fig. 1. As shown in fig. 13, the present embodiment is different from embodiment 1 in that air is introduced from a delivery path of the compressor 10 into the cooling portion 42. That is, compressed air Ar10d is introduced into cooling unit 42 instead of introducing intake air Ar32 into cooling unit 42. Therefore, the description of the cooling unit 42 and the inverter control device 40 described above can be applied to the present embodiment by replacing the intake air Ar32 with the compressed air Ar10 d.

The cooling unit 42 may be provided at any position of the delivery path of the compressed air, but the cooling unit 42 of the present embodiment is provided on the downstream side of the valve mechanism 34d (check valve). Therefore, as shown in fig. 13, a cooler 22 for cooling air is provided upstream of the cooling portion 42. In this case, since the air cooled by the cooler 22 can be introduced into the cooling portion 42, the temperature rise in the tank can be further suppressed.

As shown in fig. 13, a dehumidifier 24 for dehumidifying air is provided between the cooling unit 42 and the cooler 22. In this case, since the air dehumidified by the dehumidifier 24 can be introduced into the cooling unit 42, condensation in the tank can be prevented.

As shown in fig. 13, a valve mechanism 34d (check valve) is provided to allow the air to flow from the upstream of the cooling portion 42 to the cooling portion 42 and to block the air from flowing from the cooling portion 42 to the upstream. In this case, it is possible to prevent the backflow from the cooling unit 42 to the dehumidifier 24.

The present embodiment provides the same operation and effects as those of embodiment 1.

The above is the description of embodiment 2.

[ embodiment 3 ]

Embodiment 3 of the present invention is an air compressor. The air compression device 100 includes a compressor 10, and the compressor 10 compresses intake air and sends out compressed air, and uses the intake air or the compressed air to air-cool an electronic component. The electronic component may be the electronic component 40p of the inverter control device 40, or may be an electronic component constituting an electronic circuit other than the inverter control device 40. The method of air-cooling the electronic component may be a method of bringing a heat sink mounted on the electronic component into contact with air for cooling, or a method of bringing the electronic component into direct contact with air for cooling. The cooling may be performed in a closed space such as a tank, or may be performed in a space partially or entirely opened.

The above is the description of embodiment 3.

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. 14. 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. 14 is a front view showing the periphery of the compressor 10, and corresponds to fig. 8.

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, an example is shown in which all the air flowing through the suction path or the delivery path passes through the cooling portion 42, but the present invention is not limited to this. For example, the cooling unit 42 may be configured to pass a part of the air flowing through the intake path or the delivery path. That is, a path for bypassing a part of the air may be provided in parallel with the cooling unit 42.

In the description of the embodiment, the example of returning all the air having passed through the cooling unit 42 to the original path is shown, but the present invention is not limited to this. A part or all of the air passing through the cooling unit 42 may be discharged to the outside air, for example, without returning to the original route.

In the description of the embodiment, the motor 12 is a DC brushless motor of a surface magnet type, but the motor is not limited to this, and any motor may be used as long as it can drive the compressor, and for example, the motor may be another type of motor such as a magnet embedded type motor, an AC motor, a brush motor, or a gear motor.

In the description of the embodiment, the supply device is the inverter control device 40, but the present invention is not limited to this. The supply device may be any supply device as long as it can supply electric power to the motor, and for example, the supply device may be a plc (programmable Logic controller) that supplies electric power to the motor. In addition, the PLC is sometimes called a programmable controller or a sequence controller.

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 motor 12 is described as an example in which the stator and the rotor are respectively built in without including a bearing, but the invention is not limited thereto. For example, the motor may have a structure in which a bearing, a rotor, and a stator are integrated in a motor case.

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 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.

Claims

1. An air compression device, wherein,

this air compression device includes:

a compressor that compresses air drawn from the suction path and sends the compressed air to the sending path;

a motor that drives the compressor;

a supply device that supplies drive power to the motor; and

and a cooling unit provided in at least a part of the suction path or at least a part of the delivery path to cool the supply device.

2. The air compression device of claim 1,

the supply device has a heat sink in at least a part of the suction path or in at least a part of the discharge path.

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

the cooling part is arranged on the suction path,

a filter for suppressing passage of dust is provided upstream of the cooling section.

4. The air compression device of claim 3,

the air compression device is provided with a check valve that allows the flow of air from the cooling unit to the compressor and prevents the flow of air from the compressor to the cooling unit.

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

the cooling part is arranged on the sending-out path,

a cooler for cooling air is provided upstream of the cooling portion.

6. The air compression device of claim 5,

a dehumidifier for dehumidifying air is provided between the cooling unit and the cooler.

7. The air compressing device according to claim 5 or 6,

the air compression device is provided with a check valve that allows air to flow from upstream of the cooling portion to the cooling portion and blocks air from flowing from the cooling portion to upstream thereof.