CN111550409A

CN111550409A - Air compressor and method for manufacturing air compressor

Info

Publication number: CN111550409A
Application number: CN202010088760.8A
Authority: CN
Inventors: 黑光将; 田中源平; 川畑庆太; 久我崇
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: JP7403955B2; JP2020133403A; EP3696411B1; EP3696411A1

Abstract

The present invention relates to an air compressor and a method of manufacturing the air compressor. An object of the present invention is to provide an air compressor capable of suppressing an increase in the number of processing man-hours and reducing the residual unbalance amount. An air compression device (100) comprises: a compressor (10) that compresses air; a motor (12) that drives the compressor (10); a multi-blade fan (16) that rotates integrally with a rotor (12k) of the motor (12); a balance weight (15) which is disposed between the rotor (12k) and the multi-blade fan (16) and rotates integrally with the rotor (12 k); and balance adjustment units (15a, 15b) provided to the balance weight (15) and to which processing is applied to reduce the total unbalance amount of the balance weight (15), the rotor (12k), and the sirocco fan (16) during rotation.

Description

Air compressor and method for manufacturing air compressor

Technical Field

The present invention relates to an air compressor and a method of manufacturing the air compressor.

Background

Air compressors that generate compressed air are known. For example, patent document 1 describes an air compressor having a compressor main body that is integrated with an electric motor and is driven by the electric motor. The air compressor includes: a motor; a compressor main body that compresses air by reciprocating a piston in a cylinder by a motor; a 1 st fan disposed at a tip end of a drive shaft of the motor, the drive shaft being integrated with the rotor; and a 2 nd fan provided in the motor case.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open No. 2012 and 062846

Disclosure of Invention

Problems to be solved by the invention

In the air compressor described in patent document 1, a 1 st fan and a 2 nd fan are coupled to a drive shaft of a motor that is integrated with a rotor. In order to suppress the rotational vibration of the air compressor, the rotor of the motor, the 1 st fan, and the 2 nd fan are individually subjected to a balance adjustment process for reducing the unbalance amount. When the adjustment processing is performed individually, the total residual unbalance amount becomes large due to the accumulation of the residual unbalance amount of each member after the balance adjustment.

In order to reduce the total residual unbalance amount, it is also considered to adjust the residual unbalance amount of each component to be smaller. However, in this case, the number of steps required for adjusting the balance of each member increases, which is disadvantageous in terms of cost. That is, the reduction of the residual unbalance amount and the reduction of the cost are in the relationship of the dihedral disorder.

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 residual unbalance amount while suppressing an increase in the number of processing steps.

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; a motor driving the compressor; a fan that rotates integrally with a rotor of the motor; an intermediate member disposed between the rotor and the fan and rotating integrally with the rotor; and a balance adjustment unit provided in the intermediate member and subjected to a process for reducing the total unbalance amount of the intermediate member, the rotor, and the fan during rotation.

Another embodiment of the present invention is a method of manufacturing an air compressor assembly. The method comprises the following steps: integrating a rotor of a motor that drives a compressor for compressing air, a fan that rotates integrally with the rotor, and an intermediate member disposed between the rotor and the fan; and a step of applying a process of reducing the unbalance amount to the intermediate member integrated with the rotor and the fan.

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 residual unbalance amount while suppressing an increase in the number of processing steps.

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 the sirocco fan of the air compressing apparatus of fig. 1.

Fig. 6 is a front view showing the periphery of a balance weight of the compressor driving unit of fig. 3.

Fig. 7 is a rear view showing the periphery of the balance weight 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 flowchart illustrating a method of manufacturing 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 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 12. 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 provided on the inner peripheral side of the stationary body side concave portion 12t and is an annular wall. 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.

The multi-blade fan 16 is explained with reference to fig. 3, 4, and 5. Fig. 5 is a perspective view showing the periphery of the sirocco fan 16. The figure shows a balancing weight 15 integrated with a rotor 12k and a multi-wing fan 16. 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 rotation. 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 also explained with reference to fig. 6 and 7. Fig. 6 is a front view showing the periphery of the balance weight 15. Fig. 7 is a rear view showing the periphery of the balance weight 15. 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 frame made of metal such as brass, and also serves as the rotating body portion 12n of the labyrinth portion 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 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 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.

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 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 compresses air; a motor 12 that drives the compressor 10; a multi-blade fan 16 that rotates integrally with the rotor 12k of the motor 12; a balance weight 15 disposed between the rotor 12k and the sirocco fan 16 and rotating integrally with the rotor 12 k; and

balance adjustment units

15a and 15b provided in the balance weight 15 and subjected to processing for reducing the total unbalance amount of the balance weight 15, the rotor 12k, and the sirocco fan 16 during rotation.

According to this embodiment, as compared with the case where the rotor 12k, the sirocco fan 16, and the balance weight 15 are individually subjected to balance adjustment, it is possible to perform balance adjustment with high accuracy and reduce the total amount of unbalance. In addition, since the man-hours for individual adjustment are eliminated, the total adjustment man-hours are reduced, which is advantageous in terms of cost.

The balance weight 15 may have a fan fixing portion 15c for fixing the sirocco fan 16 and a rotor fixing portion 15d for fixing the rotor 12 k. In this case, the rotor 12k and the sirocco fan 16 can be easily integrated with the balance weight 15. In addition, compared to a case where a member for fixing the sirocco fan 16 and the rotor 12k is separately provided, the number of components is reduced, which is advantageous in terms of cost and assembly man-hours. Also, reliability is improved by reducing the number of fastening portions.

The

balance adjusting portions

15a and 15b may include a rotor-side adjusting portion 15b provided radially outward of the rotor fixing portion 15 d. In this case, since the rotor-side adjusting portion 15b is located outside the rotor fixing portion 15d, the rotor 12k does not become an obstacle during the balance adjustment, and the adjustment work is simplified.

The

balance adjustment portions

15a and 15b may include a fan-side adjustment portion 15a provided radially inward of the fan fixing portion 15 c. In this case, since the fan-side adjusting portion 15a is located inside the fan fixing portion 15c, the adjustment work is simplified without the multi-blade fan 16 being an obstacle during the balance adjustment.

The fan-side adjusting portion 15a may be provided radially inward of the plurality of blades 16 c. In this case, since the fan-side adjusting portion 15a is located inside the plurality of blades 16c, the blades 16c do not become an obstacle during the balance adjustment, and the adjustment work is simplified.

The sirocco fan 16 may be disposed between the compressor 10 and the motor 12 in the axial direction. In this case, since the multi-blade fan 16 and the compressor 10 can be connected to the output shaft 12a protruding to one side of the motor 12, the other side of the housing 12c can be closed, and the intrusion of dust into the motor 12 can be reduced.

It may be possible that the multi-wing fan 16 overlaps at least a part of the bearing supporting the rotation of the compressor 10 as viewed in the radial direction. In this case, the axial length of the air compressor 100 can be shortened in accordance with the amount of overlap.

It is possible that the multi-wing fan 16 generates an air flow for cooling air compressed in the compressor 10. In this case, the compressed air from the compressor 10 can be cooled.

The compressor 10 may be a scroll type compressor having an orbiting scroll 10n, and the rotor 12k and the orbiting scroll 10n are combined with a single rotating shaft. In this case, the air compressor device with less vibration can be provided with the reduction of the unbalance between the rotor 12k and the sirocco fan 16.

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, and since the front-rear length of the apparatus is short, a margin is generated in the underfloor space of the railway vehicle 90.

[ 2 nd embodiment ]

A method S100 for manufacturing an air compressor apparatus according to embodiment 2 of the present invention will be described with reference to fig. 13. The manufacturing method S100 of the present embodiment includes: a step S102 of integrating a rotor 12k of a motor 12 for driving a compressor 10 for compressing air, a sirocco fan 16 rotating integrally with the rotor 12k, and a balance weight 15 disposed between the rotor 12k and the sirocco fan 16; and step S104, applying processing for reducing unbalance amount to the balance weight 15 integrated with the rotor and the multi-wing fan 16.

In step S102 of integrating, the rotor 12k may be fixed to the input side of the rotor fixing portion 15d of the balance weight 15 by a fastener such as a bolt. In this step, the sirocco fan 16 may be fixed to the fan fixing portion 15c on the end surface on the opposite side to the input side of the balance weight 15 by a fastener such as a bolt. An adhesive may be applied to these fixing portions.

The unbalance amount reduction processing in step S104 is performed using the balance weight 15 integrated with the rotor 12k and the sirocco fan 16 as a workpiece. In this process, the unbalance amount of the workpiece is determined by the balance checking device, and the

balance adjusting units

15a and 15b are added or reduced in mass according to the determination result. For example, the balance can be adjusted by forming recesses in the

balance adjusters

15a and 15b with drills or the like and attaching mass bodies to the

balance adjusters

15a and 15 b.

According to the present embodiment, as compared with the case where the rotor 12k, the sirocco fan 16, and the balance weight 15 are individually subjected to balance adjustment, it is possible to perform balance adjustment with high accuracy and reduce the total amount of unbalance. In addition, since the man-hours for individually adjusting the adjustment are omitted, the total adjustment man-hours are reduced, which is advantageous in terms of cost.

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, 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. For example, the motor may be a magnet embedded motor.

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;

a motor that drives the compressor;

a fan that rotates integrally with a rotor of the motor;

an intermediate member disposed between the rotor and the fan and rotating integrally with the rotor; and

and a balance adjustment unit provided in the intermediate member, the balance adjustment unit being configured to apply a process of reducing an unbalance amount of the intermediate member, the rotor, and the fan in total during rotation.

2. The air compression device of claim 1,

the intermediate member has a fan fixing portion to which the fan is fixed and a rotor fixing portion to which the rotor is fixed.

3. The air compression device of claim 2,

the balance adjustment portion includes a rotor-side adjustment portion provided at a position radially outward of the rotor fixing portion.

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

the balance adjustment portion includes a fan-side adjustment portion provided at a position radially inward of the fan fixing portion.

5. The air compression device of claim 4,

the fan-side adjusting portion is provided radially inward of the airflow generating portion of the fan.

6. The air compressing device according to any one of claims 1 to 5,

the fan is disposed between the compressor and the motor in an axial direction.

7. The air compressing device according to any one of claims 1 to 6,

the fan overlaps at least a part of a bearing supporting rotation of the compressor as viewed in a radial direction.

8. The air compressing device according to any one of claims 1 to 7,

the compressor is a scroll type compressor having an orbiting scroll,

the rotor and the orbiting scroll are combined with a single rotating shaft.

9. A method of manufacturing an air compressor assembly, wherein,

the manufacturing method of the air compression device comprises the following steps:

integrating a rotor of a motor that drives a compressor for compressing air, a fan that rotates integrally with the rotor, and an intermediate member disposed between the rotor and the fan; and

and a step of applying a process of reducing an unbalance amount to the intermediate member integrated with the rotor and the fan.