CN117307444A - Two-stage reciprocating compressor and automobile - Google Patents
Two-stage reciprocating compressor and automobile Download PDFInfo
- Publication number
- CN117307444A CN117307444A CN202311141771.8A CN202311141771A CN117307444A CN 117307444 A CN117307444 A CN 117307444A CN 202311141771 A CN202311141771 A CN 202311141771A CN 117307444 A CN117307444 A CN 117307444A
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- Prior art keywords
- reciprocating compressor
- stage reciprocating
- housing
- rib
- intercooler
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- 230000006835 compression Effects 0.000 claims abstract description 27
- 238000007906 compression Methods 0.000 claims abstract description 27
- 238000001816 cooling Methods 0.000 description 16
- 230000000694 effects Effects 0.000 description 7
- 230000033001 locomotion Effects 0.000 description 7
- 239000000463 material Substances 0.000 description 4
- 238000005192 partition Methods 0.000 description 3
- 238000009434 installation Methods 0.000 description 2
- 238000009413 insulation Methods 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 239000000725 suspension Substances 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000010363 phase shift Effects 0.000 description 1
- 229920000915 polyvinyl chloride Polymers 0.000 description 1
- 239000004800 polyvinyl chloride Substances 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/06—Cooling; Heating; Prevention of freezing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B25/00—Multi-stage pumps
- F04B25/005—Multi-stage pumps with two cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/06—Cooling; Heating; Prevention of freezing
- F04B39/066—Cooling by ventilation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/121—Casings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B41/00—Pumping installations or systems specially adapted for elastic fluids
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The present invention relates to a two-stage reciprocating compressor and an automobile. The reciprocating compressor according to one aspect of the present invention includes: a rotation driving source accommodated in the housing; an output shaft that outputs rotation from the rotation drive source and is provided so that one end protrudes from an end surface of the housing, the output shaft extending in an axial direction; a low-pressure compression element that compresses air using a rotational driving force from the output shaft as a power source; an intercooler that cools the compressed air ejected from the low-pressure compression element; a high-pressure compression element that further compresses the compressed air cooled by the intercooler using the rotational driving force from the output shaft as a power source; and a blower fan connected to the output shaft and disposed between the end surface of the casing and the intercooler in the axial direction.
Description
The present application is a divisional application of international application number PCT/JP2019/050733 (national application number 201980086554.9), and application name "two-stage reciprocating compressor", which is 12/25 (date of entering national stage 2021/25/06).
Technical Field
The present invention relates to a two-stage reciprocating compressor.
Background
A two-stage reciprocating compressor is known in which compressed air is compressed in two stages in order to obtain compressed air at a high pressure. The two-stage reciprocating compressor has a low pressure side cylinder and a high pressure side cylinder. In the two-stage reciprocating compressor, air compressed by a low-pressure side cylinder is sent to a high-pressure side cylinder, and is further compressed in the high-pressure side cylinder. The compressed air compressed in the high-pressure side cylinder is supplied to the air compressor via the discharge port. In the case of a two-stage reciprocating compressor mounted on a commercial vehicle, compressed air discharged from a high-pressure side cylinder head is supplied to, for example, a brake or an air suspension. A conventional two-stage reciprocating compressor is disclosed in japanese patent application laid-open No. 2013-040586.
Compression heat is generated in the process of compressing air, and thus, temperatures of the cylinder and the piston rise during the operation of the reciprocating compressor. Further, the electric motor is driven by an applied current, and thus joule heat is generated by the applied current. Thereby, the temperature of the electric motor also increases. Therefore, a cooling fan is often provided in the conventional reciprocating compressor. Two-stage reciprocating compressors equipped with cooling fans are disclosed in Japanese patent application laid-open No. 9-264253 and Japanese patent application laid-open No. 2016-070233.
Prior art literature
Patent literature
Patent document 1: japanese patent laid-open No. 2013-040586
Patent document 2: japanese patent laid-open No. 9-264253
Patent document 3: japanese patent laid-open publication 2016-070233
Disclosure of Invention
Problems to be solved by the invention
Further improvement in cooling effect is required in a two-stage reciprocating compressor provided with a cooling fan.
It is an object of the present disclosure to improve the cooling effect in a two-stage reciprocating compressor. The objects of the present disclosure other than the above objects can be understood by referring to the description of the entire specification of the present application.
Solution for solving the problem
The two-stage reciprocating compressor according to an aspect of the present invention includes: a rotation driving source accommodated in the housing; an output shaft that outputs rotation from the rotation drive source and is provided so that one end protrudes from an end surface of the housing, the output shaft extending in an axial direction; a low-pressure compression element that compresses air using a rotational driving force from the output shaft as a power source; an intercooler that cools the compressed air ejected from the low-pressure compression element; a high-pressure compression element that further compresses the compressed air cooled by the intercooler using the rotational driving force from the output shaft as a power source; and a blower fan connected to the output shaft and disposed between the end surface of the casing and the intercooler in the axial direction.
In one aspect of the present invention, the housing has a plurality of ribs extending in the axial direction on an outer surface thereof.
In one aspect of the present invention, the housing has a plurality of other ribs extending in a direction perpendicular to the axial direction.
The two-stage reciprocating compressor according to an aspect of the present invention further includes a muffler for supplying the air to the low-pressure compression element.
In one aspect of the present invention, the two-stage reciprocating compressor further includes a cover that covers at least a part of the casing, the low-pressure compression element, the intercooler, the high-pressure compression element, and the blower fan.
One aspect of the present invention relates to an automobile. The automobile is provided with the two-stage reciprocating compressor.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the embodiment of the present invention, the cooling effect in the two-stage reciprocating compressor can be improved.
Drawings
Fig. 1 is a perspective view schematically showing a two-stage reciprocating compressor of an embodiment.
Fig. 2 is a schematic side view of the two-stage reciprocating compressor of fig. 1.
Fig. 3 is a sectional view schematically showing a section taken along a line A-A of the two-stage reciprocating compressor of fig. 2.
Fig. 4 is a perspective view schematically showing a two-stage reciprocating compressor of other embodiments.
Fig. 5 is a schematic cross-sectional view of a two-stage reciprocating compressor of other embodiments.
Description of the reference numerals
1. A two-stage reciprocating compressor; 10. a housing; 11. a motor housing; 12. a crankcase; 13a, 1 st cylinder (low pressure side cylinder); 13b, cylinder 2 (high pressure side cylinder); 14a, 1 st connecting rod; 14b, the 2 nd connecting rod; 15. a crankshaft; 15a, 1 st eccentric portion; 15b, 2 nd eccentric portion; 16a, 1 st piston; 16b, the 2 nd piston; 17a, 1 st cylinder cover; 17b, a 2 nd cylinder cover; 18. a leg portion; 19. a support section; 21. a front side cover; 22. a motor; 22a, stator coils; 22b, a rotor; 22c, a motor rotation shaft; 23. a rear side cover; 24. an air supply fan; 25. an intercooler.
Detailed Description
A two-stage reciprocating compressor 1 according to various embodiments of the present invention will be described with reference to fig. 1 to 3. Fig. 1 is a perspective view schematically showing a two-stage reciprocating compressor 1 according to an embodiment of the present invention, fig. 2 is a schematic side view of the two-stage reciprocating compressor 1 of fig. 1, and fig. 3 is a sectional view schematically showing a section of the two-stage reciprocating compressor 1 taken along a line A-A of fig. 2. In the case of referring to the up-down direction in the present specification, except for the case where the logic is specifically mentioned in the context, the up-down direction shown in fig. 1 is taken as a reference. In the case of referring to the front-rear direction in the present specification, the front-rear direction shown in fig. 2 is used as a reference except for the case where the logic of the front-rear is specifically mentioned. Fig. 2 shows an axis C that coincides with a central axis of a crankshaft described later. The axis C extends in the front-rear direction. In the present specification, a direction along the axis C is sometimes referred to as an axial direction, and a direction extending from the axis C perpendicularly to the axis C is sometimes referred to as a radial direction.
As shown in fig. 1, the two-stage reciprocating compressor 1 includes a housing 10. The housing 10 includes a motor case 11, a crankcase 12, a 1 st cylinder 13a, and a 2 nd cylinder 13b. The 1 st cylinder 13a and the 2 nd cylinder 13b are provided on the upper side of the crankcase 12, respectively. 4 leg portions are attached to the lower surface of the housing 10 via support portions 19. The two-stage reciprocating compressor 1 is installed at a desired installation site via the leg portion 18.
A plurality of 1 st ribs 11a extending in the axial direction and 2 nd ribs 11b extending in the up-down direction are provided on the outer surface of the motor housing 11. The upper end of the 2 nd rib 11b is connected to the front end of the corresponding 1 st rib 11 a. Some 1 st ribs 11a of the plurality of 1 st ribs 11a extend from the rear end to the front end of the motor housing 11, and the remaining 1 st ribs 11a extend forward from the rear end of the motor housing 11 and are connected to the 2 nd ribs 11b midway.
An internal space penetrating the inside of the motor housing 11 along the axis C is formed in the motor housing 11. The motor housing 11 has a substantially hollow cylindrical shape. A motor 22 is disposed in the internal space of the motor housing 11. The motor 22 has: a stator coil 22a mounted to an inner wall of the motor housing 11; a rotor 22b mounted on the radial inner side of the stator coil 22 a; and a motor rotation shaft 22c that rotates together with the rotor 22 b. The motor 22 may be provided with a rotation detection sensor that detects the rotational position of the rotor 22 b. The through hole of the motor housing 11 is closed off at the rear end by a rear side cover 23. Thereby, the rear surface of the rear side cover 23 becomes the rear end surface 11c of the motor housing 11. A through hole connecting the inner space and the outer space of the motor case 11 is provided in the center of the rear side cover 23 in the radial direction. The motor rotation shaft 22c extends to the outside of the housing 10 through a through hole provided to the rear side cover 23. The motor rotation shaft 22c is rotatably supported with respect to the motor housing 11 via a bearing.
A blower fan 24 is attached to a rear end of the motor rotation shaft 22c protruding rearward from the motor housing 11. The blower fan 24 rotates around the central axis C together with the motor rotation shaft 22C. An air flow fi flowing from the axial rear of the blower fan 24 toward the fan and an air flow fo flowing from the front of the blower fan 24 along the axial direction on the outer surface of the housing 10 are generated by the rotation of the blower fan 24.
An internal space penetrating the interior of the crankcase 12 along the axis C is formed in the crankcase 12. The inner space of the crankcase 12 is partitioned from the inner space of the motor housing 11 by a partition wall 20. The through hole provided to the crankcase 12 is blocked at its front end by a front side cover 21. The front side cover 21 has a cover main body 21a having a substantially disk shape and a dome 21b protruding forward at the center in the radial direction of the cover main body 21 a.
A crank mechanism is disposed in the inner space of the crankcase 12. The crankshaft mechanism has a crankshaft 15. The crankshaft 15 extends along the center axis C inside the crankcase 12 and the motor housing 11. The crankshaft 15 is supported at its front end by a front side cover 21. The crankshaft 15 enters the motor case 11 from a through hole provided in the partition wall 20, and is supported by the inner peripheral surface of the hollow motor rotation shaft 22c in the motor case 11. The crankshaft 15 is attached to the motor rotation shaft 22C so as to rotate around the central axis C together with the motor rotation shaft 22C. Thereby, the rotational driving force from the motor 22 is transmitted to the crankshaft 15 via the motor rotation shaft 22c.
The crankshaft 15 includes a 1 st eccentric portion 15a and a 2 nd eccentric portion 15b provided axially rearward of the 1 st eccentric portion 15 a. The 1 st eccentric portion 15a and the 2 nd eccentric portion 15b have a circular shape in a cross section viewed in a section perpendicular to the axis C. The center of the eccentric portion 15a is eccentric with respect to the axis C. The 1 st piston 16a is connected to the 1 st eccentric portion 15a via the 1 st connecting rod 14 a. Similarly, the 2 nd piston 16b is connected to the 2 nd eccentric portion 15b via the 2 nd connecting rod 14 b. The rotational motion of the crankshaft 15 is converted into the reciprocating motion of the 1 st piston 16a by the 1 st connecting rod 14a, and is converted into the reciprocating motion of the 2 nd piston 16b by the 2 nd connecting rod 14 b. Thus, the 1 st piston 16a reciprocates inside the 1 st cylinder 13a, and the 2 nd piston 16b reciprocates inside the 2 nd cylinder 13 a.
The 1 st eccentric portion 15a and the 2 nd eccentric portion 15b have different phases from each other. For example, the phase of the 1 st eccentric portion 15a and the phase of the 2 nd eccentric portion 15b are offset from each other by 180 °. When the 1 st piston 16a is driven in a direction to compress the cylinder chamber of the 1 st cylinder 13a due to this phase shift, the 2 nd piston 16b is driven in a direction to expand the cylinder chamber of the 2 nd cylinder 13b. On the other hand, when the 2 nd piston 16b is driven in a direction to compress the cylinder chamber of the 2 nd cylinder 13b, the 1 st piston 16a is driven in a direction to expand the cylinder chamber of the 1 st cylinder 13 a.
A 1 st cylinder head 17a is provided at the tip of the 1 st cylinder 13a, and a 2 nd cylinder head 17b is provided at the tip of the 2 nd cylinder 13b. The 1 st cylinder head 17a has an intake port 27a for sucking air into its inner space and an exhaust port 27b for ejecting compressed air. The internal space of the 1 st cylinder head 17a is divided into a suction chamber and a discharge chamber by a partition wall. The air flowing into the intake chamber from the outside of the 1 st cylinder head 17a through the intake port 27a is sucked into the 1 st cylinder 13a, compressed by the 1 st piston 16a reciprocating in the cylinder 13a, and discharged into the discharge chamber. The compressed air is introduced into the intercooler 25 through the pipe 26a from the exhaust port 27b of the 1 st cylinder head 17a, cooled by the intercooler 25, and then introduced into the 2 nd cylinder head 17b through the pipe 26 b. The 2 nd cylinder head 17b has an intake port 28a for taking in compressed air from the pipe 26b and an exhaust port (not shown) for discharging compressed air subjected to the second-stage compression in the 2 nd cylinder 13b. The air flowing into the 2 nd cylinder head 17b through the intake port 28a is sucked into the 2 nd cylinder 13b, is subjected to the second-stage compression by the 2 nd piston 16b reciprocating in the cylinder 13b, and is discharged to the outside of the 2 nd cylinder head 17b through the exhaust port. The compressed air compressed in two stages by the 2 nd cylinder 13b can be supplied to various air compressors not shown. Air compression machines include various devices that operate with compressed air. In the case where the two-stage reciprocating compressor 1 is mounted on a commercial vehicle, the compressed air from the 2 nd cylinder 13b can be supplied to, for example, an air brake, an air suspension, and various air compressors mounted on the commercial vehicle other than those.
In this way, in the two-stage reciprocating compressor 1, the air introduced from the outside is subjected to the first stage compression in the 1 st cylinder 13a and the second stage compression in the 2 nd cylinder 13b. Thus, the 1 st cylinder 13a is a low-pressure cylinder, and the 2 nd cylinder 13b is a high-pressure cylinder. In the present specification, the 1 st cylinder 13a is sometimes referred to as a low-pressure compression element, and the 2 nd cylinder 13b is sometimes referred to as a high-pressure compression element. The 1 st piston 16a and the 1 st cylinder head 17a may be included in the low-pressure compression element. The high-pressure compression element may include a 2 nd piston 16b and a 2 nd cylinder head 17b.
As shown in fig. 3, the intercooler 25 is provided at a position rearward of the blower fan 24 in the axial direction. In other words, the blower fan 24 is provided between the intercooler 25 and the rear end surface of the motor housing 11. The intercooler 25 is attached to the motor housing 11 by, for example, a bolt not shown.
The intercooler 25 is connected to the exhaust port 27b of the 1 st cylinder head 17a via a pipe 26a, and is connected to the intake port 28a of the 2 nd cylinder head 17b via a pipe 26 b. The intercooler 25 has a meandering pipe connecting the pipe 26a and the pipe 26b and a plurality of fins provided to the pipe. The high-temperature compressed air compressed in the 1 st cylinder 13a is supplied from the pipe 26a to the pipe of the intercooler 25. As described above, the airflow fi flows with the rotation of the blower fan 24, and the airflow passes through the intercooler 25. The air flow fi flows along the outer surfaces of the piping of the intercooler 25 and the outer surfaces of the fins, and therefore, the compressed air passing through the inside of the intercooler 25 is cooled.
Next, the operation of the two-stage reciprocating compressor 1 will be described. When a current is applied to the stator coil 22a, the rotor 22b rotates with respect to the stator coil 22 a. At this time, the rotation of the rotor 22b is transmitted to the crankshaft 15 and the blower fan 24 via the motor rotation shaft 22c. The rotational motion of the crankshaft 15 is converted into the reciprocating motion of the 1 st piston 16a by the 1 st connecting rod 14a, and is converted into the reciprocating motion of the 2 nd piston 16b by the 2 nd connecting rod 14 b. By the reciprocating motions of the 1 st and 2 nd pistons 16a and 16b, air introduced from the outside is subjected to first-stage compression in the 1 st cylinder 13a and second-stage compression in the 2 nd cylinder 13b. The air compressed in the 1 st cylinder 13a is cooled by the intercooler 25 and then introduced into the 2 nd cylinder 13b. Cooling air is supplied from an air blower fan 24 rotated by a rotational driving force from a motor 22 to an intercooler 25.
Fig. 4 is a perspective view showing a two-stage reciprocating compressor 1 according to another embodiment of the present invention. The two-stage reciprocating compressor 1 of fig. 4 is different from the two-stage reciprocating compressor 1 shown in fig. 1 in that it is provided with a cover 40. The cover 40 is a sound-proof cover. The cover 40 may also cover the entire circumference of the two-stage reciprocating compressor 1. In the illustrated embodiment, the leg portions 18 in the two-stage reciprocating compressor 1 are exposed with respect to the cover 40 for ease of installation to the vehicle body. The cover 40 may be provided with a through hole in a part thereof, which connects the inside and the outside of the cover 40. The cover 40 is formed of a material having a sound insulation function. The cover 40 is made of, for example, felt, polyvinyl chloride, or a material having sound insulation other than them. The cover 40 can suppress leakage of sound generated from the two-stage reciprocating compressor 1 to the outside.
Fig. 5 is a cross-sectional view showing a two-stage reciprocating compressor 1 according to another embodiment of the present invention. The two-stage reciprocating compressor 1 of fig. 5 is different from the two-stage reciprocating compressor 1 shown in fig. 1 in that a muffler 50 is provided. The muffler 50 is mounted to the dome 21b of the front cover 21. The muffler 50 has, for example, a hollow cylindrical shape. The internal space of the muffler 50 is divided into a 1 st chamber into which external air is introduced from the air inlet 50a and a muffler chamber connected to the 1 st chamber and into which air is introduced from the 1 st chamber. The air inlet 50a can be provided at an arbitrary position of the muffler 50. The internal space of the muffler 50 may have a divided space other than the 1 st chamber and the muffling chamber. The muffling chamber is connected to the intake port 27a of the 1 st cylinder head 17a. When the motor 22 is driven, the suction chamber of the 1 st cylinder head 17a is negative pressure, and therefore, air is introduced into the 1 st chamber from the outside of the muffler 50. The air enters the muffling chamber from chamber 1. The air expands in the muffling chamber and is thus muffled. Thus, intake noise generated when outside air is sucked can be reduced.
The two-stage reciprocating compressor 1 described above can be mounted on a commercial vehicle, for example. One embodiment of the present invention is an automobile provided with a two-stage reciprocating compressor 1.
The operational effects of the above-described embodiment will be described below. In one embodiment of the present invention, the blower fan 24 is provided between the rear end surface 11c of the motor housing 11 and the intercooler 25 in the axial direction. As a result, the cooling air generated by the blower fan 24 is liable to pass through the intercooler 25, and therefore the cooling effect of the compressed air in the intercooler 25 is improved. In the conventional two-stage reciprocating compressor, an intercooler is provided between the rear end surface of the motor housing and the blower fan in the axial direction. In this conventional two-stage reciprocating compressor arrangement, the cooling air sent from the blower fan to the intercooler collides with the rear end surface of the motor housing, and the air flow is disturbed, and the cooling air from the blower fan does not sufficiently contribute to the cooling of the intercooler. In the embodiment of the present invention, the cooling effect is improved by changing the arrangement of the blower fan and the intercooler in the axial direction.
In the above-described embodiment, the plurality of 1 st ribs 11a extending in the axial direction and the plurality of 2 nd ribs 11b extending in the up-down direction are provided on the outer surface of the motor housing 11. In the operation of the two-stage reciprocating compressor 1, joule heat is generated by the applied current applied to the stator coil 22a, and the heat generated at the stator coil 22a is transferred to the motor housing 11. Since the surface area of the outer surface of the motor case 11 is increased by the 1 st rib 11a and the 2 nd rib 11b, heat generated in the stator coil 22a can be efficiently dissipated to the atmosphere.
In addition, the 1 st rib 11a guides cooling air from the blower fan 24 in the axial direction along the outer surface of the motor housing 11. Accordingly, the cooling air from the blower fan 24 flows between the adjacent 1 st ribs 11a, and therefore, the heat radiation efficiency can be further improved by the cooling air.
The dimensions, materials, and arrangements of the components described in the present specification are not limited to those explicitly described in the embodiments, and the components may be modified to have any dimensions, materials, and arrangements that can be included in the scope of the present invention. In addition, components not explicitly described in the present specification may be added to the described embodiments, and a part of the components described in each embodiment may be omitted.
Part of the modified examples will be described below. The motor housing 11 and the crankcase 12 may also have an integral, one-piece construction. The motor housing 11 and the crankcase 12 may be formed as separate members. The two-stage reciprocating compressor 1 may also be provided with a control circuit for controlling the motor 22.
Claims (6)
1. A two-stage reciprocating compressor is provided with:
a rotation driving source accommodated in the housing;
an output shaft that outputs rotation from the rotation drive source and is provided so that one end protrudes from an end surface of the housing, the output shaft extending in an axial direction;
a low-pressure compression element that compresses air using a rotational driving force from the output shaft as a power source;
an intercooler that cools the compressed air ejected from the low-pressure compression element;
a high-pressure compression element that further compresses the compressed air cooled by the intercooler using the rotational driving force from the output shaft as a power source; and
a blower fan connected to the output shaft and disposed between the end surface of the casing and the intercooler in the axial direction,
a plurality of 1 st ribs extending in the axial direction and a plurality of 2 nd ribs extending in a direction perpendicular to the axial direction are provided on an outer surface of the housing.
2. The two-stage reciprocating compressor of claim 1 wherein,
the two-stage reciprocating compressor further includes a muffler for supplying the air to the low-pressure compression element.
3. The two-stage reciprocating compressor of claim 1 or 2, wherein,
the two-stage reciprocating compressor further includes a cover that covers at least a part of the casing, the low-pressure compression element, the intercooler, the high-pressure compression element, and the blower fan.
4. The two-stage reciprocating compressor of claim 1 wherein,
of the plurality of 1 st ribs in question,
a part of the 1 st rib is the 1 st rib extending from the rear end to the front end of the housing,
the remaining 1 st rib is a 1 st rib extending from the rear end of the housing toward the front and connected halfway with a corresponding 2 nd rib of the plurality of 2 nd ribs.
5. The two-stage reciprocating compressor of claim 1 wherein,
of the plurality of 1 st ribs in question,
a part of the 1 st rib is a 1 st rib extending from a rear end to a front end of the housing and having a front end located at the front end, and a 1 st rib extending from the rear end to the front end of the housing and having a front end located at the front end and connected to an upper end of a corresponding 2 nd rib of the plurality of 2 nd ribs,
the remaining 1 st rib includes a 1 st rib extending from the rear end of the housing toward the front and having a front end connected midway with an upper end of a corresponding 2 nd rib of the plurality of 2 nd ribs.
6. An automobile provided with the two-stage reciprocating compressor according to any one of claims 1 to 5.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018-245041 | 2018-12-27 | ||
| JP2018245041 | 2018-12-27 | ||
| CN201980086554.9A CN113646535B (en) | 2018-12-27 | 2019-12-25 | Two-stage reciprocating compressor |
| PCT/JP2019/050733 WO2020138129A1 (en) | 2018-12-27 | 2019-12-25 | Two-stage reciprocating compressor |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201980086554.9A Division CN113646535B (en) | 2018-12-27 | 2019-12-25 | Two-stage reciprocating compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN117307444A true CN117307444A (en) | 2023-12-29 |
Family
ID=71129429
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311141771.8A Pending CN117307444A (en) | 2018-12-27 | 2019-12-25 | Two-stage reciprocating compressor and automobile |
| CN201980086554.9A Active CN113646535B (en) | 2018-12-27 | 2019-12-25 | Two-stage reciprocating compressor |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201980086554.9A Active CN113646535B (en) | 2018-12-27 | 2019-12-25 | Two-stage reciprocating compressor |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP3904684B1 (en) |
| JP (1) | JPWO2020138129A1 (en) |
| CN (2) | CN117307444A (en) |
| WO (1) | WO2020138129A1 (en) |
Family Cites Families (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2899130A (en) * | 1959-08-11 | Compressor | ||
| FR980379A (en) * | 1948-03-20 | 1951-05-11 | Improvements to compressor devices, in particular those intended for cold production | |
| AT338955B (en) * | 1976-02-05 | 1977-09-26 | List Hans | SINGLE-ACTING COMPRESSOR |
| JPS61145887U (en) * | 1985-03-04 | 1986-09-09 | ||
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| US8128379B2 (en) * | 2008-11-19 | 2012-03-06 | Wabtec Holding Corp. | Temperature management system for a 2CD type air compressor |
| US9856866B2 (en) * | 2011-01-28 | 2018-01-02 | Wabtec Holding Corp. | Oil-free air compressor for rail vehicles |
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| JP6390318B2 (en) | 2014-09-30 | 2018-09-19 | 工機ホールディングス株式会社 | air compressor |
| CN105464939B (en) * | 2015-12-17 | 2018-11-02 | 珠海格力电器股份有限公司 | Sound-proof housing of compressor |
| CN106150971A (en) * | 2016-07-22 | 2016-11-23 | 瑞立集团瑞安汽车零部件有限公司 | A kind of two stages of compression vehicle piston oilless air compressor |
| CN106837734A (en) * | 2017-03-22 | 2017-06-13 | 周登荣 | A kind of level Four W type high pressure compressors |
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2019
- 2019-12-25 CN CN202311141771.8A patent/CN117307444A/en active Pending
- 2019-12-25 CN CN201980086554.9A patent/CN113646535B/en active Active
- 2019-12-25 JP JP2020563332A patent/JPWO2020138129A1/en active Pending
- 2019-12-25 EP EP19904221.9A patent/EP3904684B1/en active Active
- 2019-12-25 WO PCT/JP2019/050733 patent/WO2020138129A1/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| CN113646535B (en) | 2023-09-22 |
| EP3904684B1 (en) | 2024-02-14 |
| CN113646535A (en) | 2021-11-12 |
| WO2020138129A1 (en) | 2020-07-02 |
| EP3904684A4 (en) | 2022-09-07 |
| JPWO2020138129A1 (en) | 2021-11-11 |
| EP3904684A1 (en) | 2021-11-03 |
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