阅读说明：本技术 空气压缩装置 (Air compressor ) 是由 黑光将 久我崇 川畑庆太 田中源平 于 2020-02-12 设计创作，主要内容包括：本发明涉及一种空气压缩装置。本发明是鉴于与压缩空气的冷却相关的课题而做成的,其一个目的在于提供一种能够抑制大型化并且能够高效地冷却在压缩机中被压缩后的空气的空气压缩装置。空气压缩装置(100)包括：压缩机(10),其生成压缩空气；马达(12),其驱动压缩机(10)；多翼风扇(16),其被马达(12)驱动而生成空气流；第1冷却器(18),其冷却压缩空气；以及第2冷却器(20),其利用空气流冷却在第1冷却器(18)中被冷却后的压缩空气,第1冷却器(18)利用冷却了第2冷却器(20)的空气流冷却压缩空气。(The present invention relates to an air compressor. The present invention has been made in view of the problems associated with cooling compressed air, and an object thereof is to provide an air compression device capable of efficiently cooling air compressed in a compressor while suppressing an increase in size. An air compression device (100) comprises: a compressor (10) that generates compressed air; a motor (12) that drives the compressor (10); a multi-blade fan (16) that is driven by the motor (12) to generate an air flow; a 1 st cooler (18) that cools the compressed air; and a 2 nd cooler (20) that cools the compressed air cooled in the 1 st cooler (18) with an air flow, and the 1 st cooler (18) cools the compressed air with the air flow that has cooled the 2 nd cooler (20).)

1. An air compression device, wherein,

this air compression device includes:

a compressor that generates compressed air;

a motor that drives the compressor;

a fan driven by the motor to generate an air flow;

a 1 st cooler that cools the compressed air; and

a 2 nd cooler that cools the compressed air cooled in the 1 st cooler with the air flow,

the 1 st cooler cools the compressed air using the air stream that cooled the 2 nd cooler.

2. The air compression device of claim 1,

the fan is disposed between the motor and the compressor.

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

the 1 st cooler and the 2 nd cooler are arranged along a direction orthogonal to the rotation axis of the fan.

4. The air compression device of claim 3,

the 1 st cooler is integrally disposed on a side of the 2 nd cooler opposite to the fan.

5. The air compression device of claim 4,

the air flow flows around the 1 st cooler and the 2 nd cooler which are integrally arranged in a direction orthogonal to the rotation axis of the fan.

6. An air compression device, wherein,

the air compression device includes a cooler including a front-stage cooler and a rear-stage cooler that sequentially cool compressed air generated in a compressor, the front-stage cooler cooling the compressed air with an air flow that cools the rear-stage cooler.

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 for cooling the compressor main body. An aftercooler for cooling air compressed in the scroll compressor body is disposed on the rear surface of the compressor.

Disclosure of Invention

Problems to be solved by the invention

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

The air compressed in the compressor body is at a high temperature of 200 ℃ or higher, and is desirably cooled to room temperature during use. In the air compressor described in patent document 1, the aftercooler is cooled by cooling air of the cooling fan that cools the scroll compressor main body. That is, the cooling air of the cooling fan is used for both cooling the compressor main body and cooling the aftercooler. When the compressor main body is sufficiently cooled, the temperature of the cooling air after cooling increases, and then the cooling of the cooler becomes insufficient. On the other hand, if the aftercooler is to be sufficiently cooled, the cooling of the compressor main body becomes insufficient.

In order to sufficiently cool the compressor main body and the after cooler, it is also conceivable to increase the size of the cooling fan. However, in this case, the demand for downsizing of the air compressor device equipped with the cooling fan is violated. That is, sufficient cooling of the aftercooler is in a two-bar reflex relationship with miniaturization of the device.

Thus, the present inventors have recognized that there is room for improvement in terms of efficiently cooling compressed air in an air compression device.

The present invention has been made in view of the above problems, and an object thereof is to provide an air compression device capable of efficiently cooling air compressed in a compressor while suppressing an increase in size.

Means for solving the problems

In order to solve the above problem, an air compressor according to an embodiment of the present invention includes: a compressor that generates compressed air; a motor driving the compressor; a fan driven by the motor to generate an air flow; a 1 st cooler that cools the compressed air; and a 2 nd cooler that cools the compressed air cooled in the 1 st cooler with an air flow. The 1 st cooler cools the compressed air using the air stream that cools the 2 nd cooler.

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 compression device capable of efficiently cooling air compressed in a compressor while suppressing an increase in size.

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

Fig. 5 is a schematic view illustrating the flow of air of the cooler of fig. 4.

Fig. 6 is a side sectional view showing an enlarged periphery of a labyrinth portion of the compressor driving portion of fig. 3.

Fig. 7 is a perspective view showing the periphery of the sirocco fan of the air compressing apparatus of fig. 1.

Fig. 8 is a front view showing the periphery of a balance weight of the compressor driving unit of fig. 3.

Fig. 9 is a rear view showing the periphery of the balance weight of the compressor driving part of fig. 3.

Fig. 10 is a front view schematically showing a compressor and a blower fan of the air compressing device of fig. 1.

Fig. 11 is another front view schematically showing a compressor and a blower fan of the air compressing device of fig. 1.

Fig. 12 is a view schematically showing the flow of air from the blower fan of fig. 10.

Fig. 13 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 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 10 generates compressed air. The compressor driving unit 14 includes a motor 12 for driving 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 that is used for cooling in cooler 22. The multi-bladed fan 16 is sometimes referred to as a sirocco fan. The air introduction portion 26 introduces compressed air into the motor 12. The blower fan 28 generates an air flow that cools 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 cooler 22 is explained with reference to fig. 2 to 5. 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 perspective view schematically showing the cooler 22. Fig. 5 is a schematic diagram illustrating the flow of air of the cooler 22. 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 of the present embodiment includes a 1 st cooler 18 and a 2 nd cooler 20 that sequentially cool the compressed air generated in the compressor 10. The 1 st cooler 18 is a front-stage cooler provided in a front stage of the 2 nd cooler 20, and the 2 nd cooler 20 is a rear-stage cooler provided in a rear stage of the 1 st cooler 18. The 2 nd cooler 20 is sometimes referred to as an aftercooler and the 1 st cooler 18 is sometimes referred to as a precooler. The 2 nd cooler 20 secondarily cools the compressed air cooled in the 1 st cooler 18 by the air flow Ar16a generated by the sirocco fan 16. The 1 st cooler 18 primarily cools the compressed air from the compressor 10 with the air flow Ar16b used for cooling in the 2 nd cooler 20.

The 1 st cooler 18 and the 2 nd cooler 20 may be disposed at any position as long as a desired cooling effect can be obtained. The 1 st cooler 18 and the 2 nd cooler 20 of the present embodiment are disposed above the center in the vertical direction of the air compression device 100. The 1 st cooler 18 and the 2 nd cooler 20 may be arranged in a direction orthogonal to the rotation axis of the sirocco fan 16. In particular, the 1 st cooler 18 and the 2 nd cooler 20 are disposed above the sirocco fan 16 and between the floor of the railway vehicle 90. The path of the air flow Ar16a sent from the sirocco fan 16 is shortened, and an extra piping space is omitted. Further, the front-rear length of the air compressor 100 can be shortened as compared with the case where the air compressor is disposed along the front-rear direction of the sirocco fan 16.

The 1 st cooler 18 and the 2 nd cooler 20 may be disposed separately, but in the present embodiment, the 1 st cooler 18 may be disposed on the opposite side of the 2 nd cooler 20 from the sirocco fan 16. In this example, the 1 st cooler 18 is integrally disposed above the 2 nd cooler 20 in a stacked manner. By disposing the 1 st cooler 18 and the 2 nd cooler 20 integrally, the heat-resistant connecting hose between the two can be shortened or omitted. The air flow may flow around the 1 st cooler 18 and the 2 nd cooler 20 in a direction orthogonal to the rotation axis of the sirocco fan 16. In this example, the airflow from the multi-blade fan 16 flows through the 1 st cooler 18 and the 2 nd cooler 20, which are integrally arranged, from the bottom to the top.

The detailed structure of the 1 st cooler 18 and the 2 nd cooler 20 will be explained. 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 18e by a heat-resistant connecting hose. 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 compressor driving unit 14 will be described with reference to fig. 2, 3, and 6. Fig. 6 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.

The multi-blade fan 16 is explained with reference to fig. 3, 6, and 7. Fig. 7 is a perspective view showing the periphery of the sirocco fan 16. The figure shows a balance weight 15 that integrates a rotor 12k and a sirocco 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 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. 6, 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. 8 and 9. Fig. 8 is a front view showing the periphery of the balance weight 15. Fig. 9 is a rear view showing the periphery of the balance weight 15. 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. 8 and 9, 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 10 to 12. These drawings show the compressor 10 and the blower fan 28 as viewed from an arrow F of fig. 2. Fig. 10 is a front view schematically showing the compressor 10 and the blower fan 28. Fig. 11 shows a state where the fixed scroll portion 10j is removed. Fig. 12 shows the back space 10g with the orbiting scroll 10h removed. The compressor 10 of the present embodiment is a scroll-type air compressor including a rotary shaft 10a, a main body portion 10b, an intake port 10c, an exhaust port 10e, air cooling fins 10f, a orbiting scroll portion 10h, a fixed scroll portion 10j, and a back space 10 g.

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

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

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

The blower fan 28 will be described with reference to fig. 2, 10 to 12. 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. 12, the blower fan 28 is disposed on the side of the compressor 10 such that the rotation axis L28 of the propeller 28b is orthogonal 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 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 generates compressed air; a motor 12 that drives the compressor 10; a multi-wing fan 16 driven by the motor 12 to generate an air flow; a 1 st cooler 18 that cools the compressed air; and a 2 nd cooler 20 that cools the compressed air cooled in the 1 st cooler 18 with an air flow, and the 1 st cooler 18 cools the compressed air with the air flow that has cooled the 2 nd cooler 20.

According to this embodiment, since the 1 st cooler 18 is provided, the 2 nd cooler 20 can be made small and light. In addition, since the 1 st cooler 18 is provided, the temperature of the input air to the 2 nd cooler 20 is low, and therefore, the thermal stress of the 2 nd cooler 20 can be relaxed.

In addition, the 1 st cooler 18 can effectively use the exhaust gas cooled by the 2 nd cooler 20. In addition, since the temperature difference between the cooled air and the cooling air in the 1 st cooler 18 is reduced, the thermal stress of the 2 nd cooler 20 can be relaxed. In addition, since the temperature difference between the cooled air and the cooling air in the 2 nd cooler 20 is large, the efficiency of heat exchange can be improved.

Multi-blade fan 16 may be disposed between motor 12 and compressor 10. In this case, if the sirocco fan 16 is provided on the opposite side of the compressor 10 with respect to the motor 12, it is necessary to provide projections on both the front and rear sides of the shaft of the motor 12, and in this arrangement, one projection can be omitted. Since the number of the protruding portions is reduced, the intrusion of dust into the motor 12 from the gaps of the protruding portions is reduced.

The 1 st cooler 18 and the 2 nd cooler 20 may be arranged along a direction orthogonal to the rotation axis of the sirocco fan 16. In this case, the flow path of the air flow from the sirocco fan 16 to the 1 st cooler 18 and the 2 nd cooler 20 becomes short, and the efficiency of the sirocco fan 16 is improved. The flow path of the air flow can be simplified.

The 1 st cooler 18 may be integrally disposed on the opposite side of the 2 nd cooler 20 from the sirocco fan 16. In this case, by disposing the 1 st cooler 18 and the 2 nd cooler 20 integrally, a heat-resistant connection hose connecting the two can be shortened or omitted.

The air flow may flow around the 1 st cooler 18 and the 2 nd cooler 20 integrally disposed in a direction orthogonal to the rotation axis of the fan. In this case, the flow path of the air flow becomes short, the flow path resistance decreases, and the efficiency of the sirocco fan 16 improves. The flow path of the air flow can be simplified.

The present air compressor device 100 may be an air compressor device for a railway vehicle mounted under the floor of the railway vehicle 90, and the sirocco fan 16 may send an air flow in a direction orthogonal to the traveling direction of the railway vehicle 90. In this case, the compressed air can be used in the vehicle 90. Further, since the air flow is sent in the orthogonal direction, the variation in the flow velocity of the air flow caused by acceleration and deceleration of the vehicle 90 can be alleviated. Further, when the vehicle 90 travels, dust that flies in the traveling direction and enters the 1 st cooler 18 and the 2 nd cooler 20 can be reduced.

The above is the description of embodiment 1.

[ 2 nd embodiment ]

Embodiment 2 of the present invention is also an air compressor. The air compression device 100 includes a cooler including a front-stage cooler and a rear-stage cooler that sequentially cool compressed air generated in the compressor 10, and the front-stage cooler cools the compressed air using an air flow that cools the rear-stage cooler. For example, the front stage cooler may be the 1 st cooler 18 and the back stage cooler may be the 2 nd cooler 20. The cooled compressed air may be cooled using an air flow generated by a multi-wing fan 16.

According to embodiment 2, the same operation and effects as those of embodiment 1 are obtained.

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 200 according to a modification 1 will be described with reference to fig. 13. 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. 13 is a front view showing the periphery of the compressor 10, and corresponds to fig. 10.

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 coolers 18 and 20 are examples of heat exchangers in which the tubes through which the air to be cooled flows are brought into contact with the cooling air, but the present invention is not limited to this. The cooler may also be based on other principles. For example, the cooler may be configured such that cooling fins provided on the tubes are brought into contact with the cooling air, two metal plates sandwiching the cooling air may be brought into contact with the cooling air, or a double tube may be used.

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

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

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

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.

The modification described above has the same operation and effect 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.