WO2017195576A1

WO2017195576A1 - Piston-type compressor

Info

Publication number: WO2017195576A1
Application number: PCT/JP2017/016080
Authority: WO
Inventors: 和弘真島; 心吾星崎
Original assignee: 株式会社コガネイ
Priority date: 2016-05-12
Filing date: 2017-04-21
Publication date: 2017-11-16
Also published as: JP2017203428A; TW201740020A; JP6526600B2

Abstract

A piston-type compressor (10a) includes a compressor assembly (12) comprising: a cylinder block (21) provided with a plurality of pistons; an adapter (26) provided with an air intake communication hole and a discharge communication hole that communicate with a pump chamber; and a drive shaft (16) that drives the pistons. In the compressor assembly (12), a main shaft (14) and a drive shaft (16) of an electric motor (13) pass through a support plate (11) and are mounted on the front side of the support plate (11). A power transmission mechanism (19) that transmits the rotation of the main shaft (14) to the drive shaft (16) is disposed on the back side of the support plate (11), and a channel member (20) for guiding air discharged from the pump chamber to the outside is attached to the back of the support plate (11).

Description

Piston compressor

The present invention relates to a piston type compressor for compressing a gas such as air by reciprocating movement of a piston.

Compressors used to compress gas such as air include a piston type in which the pump chamber is expanded and contracted by reciprocating movement of the piston. Patent Document 1 describes a piston type compressor having four pistons. The compressor has a piston case, and four cylinder holes into which the pistons are incorporated are provided in the piston case, and the four cylinder holes are arranged in a cross shape on the same plane. A cam member disposed at the center of the four cylinder holes is provided on the drive shaft. A main shaft of an electric motor for rotationally driving the drive shaft is connected coaxially with the drive shaft. Patent Document 2 describes a reciprocating compressor including four cylinders each provided with a piston. In this reciprocating compressor, four pistons are provided in a cylinder while being shifted in the axial direction on an eccentric shaft fixed to a motor shaft.

Patent Document 3 describes a pump mechanism including two pumps. In this pump mechanism, the two pumps are mounted on the surface side of the base so that the pump rotating shaft is parallel to the base, and an electric motor is mounted on the back side of the base. A belt is stretched between a drive wheel attached to the drive shaft of the electric motor and a pulley attached to each pump shaft, and the belt passes through a through hole provided in the base. Patent Document 4 describes a reciprocating compressor including a compressor body attached to an air tank. In this reciprocating compressor, the compressor body and the electric motor are attached to the air tank in parallel with each other, a drive pulley attached to the drive shaft of the motor, and a driven pulley attached to the crankshaft of the compressor body A belt is stretched around.

Patent Document 5 describes a belt guard set for a belt-driven reciprocating compressor. The compressor body and the electric motor are attached to a base or the like in parallel with each other. In this compressor, a V-belt is stretched between a flywheel pulley attached to the drive shaft of the reciprocating compressor and a motor pulley, and a belt guard set covering each pulley and V-belt is divided into modules. And resin molding.

JP 2016-23555 A JP 2009-185789 A Japanese Patent Laid-Open No. 10-288159 JP 2007-92680 A JP-A-8-270565

As described in Patent Document 1, if the drive shaft of the compressor and the drive shaft of the electric motor for rotationally driving the compressor are arranged coaxially, the axial dimension of the compressor including the electric motor cannot be reduced. . Further, as described in Patent Document 2, if the four pistons are arranged offset in the axial direction with respect to the eccentric shaft, the axial dimension of the reciprocating compressor including the motor cannot be reduced. Further, as described in Patent Document 3, two pumps are mounted on the surface side of the base so that the pump rotating shaft is parallel to the base, and an electric motor is mounted on the back side of the base. However, the vertical dimension of the pump mechanism cannot be reduced.

Also in the reciprocating compressors described in Patent Documents 4 and 5, it is necessary to attach the electric motor and the compressor main body to members such as an air tank, and the compressor main body including the electric motor cannot be reduced in size. In addition, when a plurality of cylinders are provided in the compressor body, it is necessary to circulate the air supply piping for supplying air to each cylinder and the discharge piping discharged from the cylinders around the compressor body. The structure of the machine becomes complicated. Furthermore, each pipe becomes a vibration source when the compressor body is driven, and vibration noise from the reciprocating compressor increases.

An object of the present invention is to reduce the size and thickness of a piston type compressor.

A piston type compressor of the present invention drives a cylinder block provided with a plurality of pistons for expanding and contracting a pump chamber, an adapter provided with an intake communication hole and a discharge communication hole communicating with the pump chamber, and the piston. A piston-type compressor including a compressor assembly having a drive shaft, wherein the main shaft of the electric motor that drives the drive shaft and the drive shaft penetrate, and the compressor assembly and the electric motor are mounted on the surface side A support plate, a power transmission mechanism that is disposed on the back side of the support plate and transmits the rotation of the main shaft to the drive shaft, and is attached to the back surface of the support plate and communicates with the discharge communication hole. A flow path member for guiding the gas discharged from the pump chamber to the outside.

The compressor assembly and the electric motor are mounted on the surface side of the support plate, and the power transmission mechanism for transmitting the rotation of the main shaft of the electric motor to the drive shaft of the compressor assembly is arranged on the back side of the support plate. The thickness dimension of the piston compressor in the direction perpendicular to the plate can be reduced. Thereby, a piston type compressor can be reduced in size and thickness.

It is a perspective view which shows the 1st surface side of the piston type compressor which is one Embodiment. It is a perspective view which shows the 2nd surface side of FIG. It is a front view which shows the 1st surface side of FIG. It is a front view which shows the 2nd surface side of FIG. It is a left view of FIG. FIG. 6 is an enlarged sectional view taken along line AA in FIG. FIG. 6 is a sectional view taken along line BB in FIG. FIG. 4 is an enlarged sectional view taken along line CC in FIG. 3. FIG. 9 is a perspective view of the compressor assembly shown in FIG. 8. (A) is the D section enlarged front view in FIG. 3, (B) is a side view of the arrow E direction of (A). (A) is a cross-sectional view taken along line FF in FIG. 10 (B), and (B) is a cross-sectional view taken along line GG in (A). FIG. 11A is a cross-sectional view taken along the line HH in FIG. 11B, and FIG. 11B is a cross-sectional view taken along the line II in FIG. It is a front view which shows the modification of a compressor assembly. It is the JJ sectional view taken on the line in FIG. FIG. 15 is a perspective view of FIG. 14. It is a perspective view which shows the 1st surface side of the piston type compressor which is other embodiment. It is a perspective view which shows the 2nd surface side of FIG. It is a front view which shows the 1st surface side of FIG. It is a front view which shows the 2nd surface side of FIG. FIG. 17 is a left side view of FIG. 16. FIG. 21 is a sectional view taken along line KK in FIG. 20. It is the LL sectional view taken on the line in FIG. FIG. 19 is a sectional view taken along line MM in FIG.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In each figure, the same code | symbol is attached | subjected to the member which has a common function.

As shown in FIGS. 1 to 5, the piston compressor 10 a has a rectangular support plate 11. The compressor assembly 12 and the electric motor 13 are mounted on the first surface 11 a side of the support plate 11. The electric motor 13 is an outer rotor type, and the main shaft 14 of the electric motor 13 passes through the support plate 11 and protrudes toward the second surface 11b of the support plate 11, and a drive pulley 15 as a drive side rotating body is provided with the main shaft 14. It is fixed to the tip. The drive shaft 16 of the compressor assembly 12 passes through the support plate 11 and protrudes toward the second surface 11b, and a driven pulley 17 as a driven side rotating body is fixed to the tip of the drive shaft 16. In the specification, the support plate 11 has a first surface 11a on which the compressor assembly 12 and the electric motor 13 are mounted as a front surface and an opposite second surface 11b as a back surface.

A timing belt 18 as a power transmission member is stretched between the drive pulley 15 and the driven pulley 17, and the drive shaft 16 is rotationally driven by the electric motor 13 via the timing belt 18. Both the driving pulley 15 and the driven pulley 17 and the timing belt 18 are disposed on the back side of the support plate 11. Both pulleys and the timing belt 18 form a power transmission mechanism 19 for transmitting the rotational torque of the main shaft 14 of the electric motor 13 to the drive shaft 16. The flow path member 20 is attached to the back surface of the support plate 11. As shown in FIG. 4, the flow path member 20 includes a parallel portion 20 a extending along the left and right sides of the support plate 11 so as to surround the driven pulley 17, and one end portion of these parallel portions 20 a. And a connecting portion 20b. The flow path member 20 includes two parallel portions 20a and one connecting portion 20b. A flow path for guiding the gas discharged from the compressor assembly 12 to the outside is provided in the flow path member 20. The flow path member 20 is formed of a member having a rectangular cross section, and the strength of the support plate 11 is increased by attaching the flow path member 20 to the support plate 11. Thereby, the support plate 11 can be comprised with a thin board | plate material.

As shown in FIGS. 6 and 8, the compressor assembly 12 includes a cylinder block 21, and the cylinder block 21 has a hexagonal outer peripheral surface. A cam housing chamber 22 is provided at the center of the cylinder block 21, and a cam member 23 is incorporated into the cam housing chamber 22. The cam member 23 is attached to the drive shaft 16, and the cam member 23 is rotationally driven by the drive shaft 16. As shown in FIG. 8, the rotation center axis O of the drive shaft 16 is perpendicular to the support plate 11, and the drive shaft 16 is attached to protrude on the back side of the support plate 11. Six cylinder holes 24 are provided in the cylinder block 21 in a direction crossing the cam housing chamber 22. The cylinder holes 24 are provided in the cylinder block 21 at intervals of 60 degrees in the direction along the outer peripheral surface of the cylinder block 21. Of the six cylinder holes 24, two cylinder holes 24 provided coaxially form a pair, and three pairs of cylinder holes 24 are provided in the cylinder block 21. The center axis of the cylinder hole 24 is orthogonal to the rotation center axis O of the drive shaft 16. The inner end of the cylinder hole 24 communicates with the cam housing chamber 22, and the outer end opens on the outer peripheral surface of the cylinder block 21.

The cylinder block 21 has six mounting surfaces 25, and the outer end of the cylinder hole 24 is open to the mounting surface 25. The adapter 26 is attached to each mounting surface 25 by a screw member 27. The adapter 26 includes a magnet holder 28 that is in contact with the mounting surface 25 and a flow path plate 29 that is attached to the magnet holder 28. The magnet holder 28 and the flow path plate 29 are each formed of a nonmagnetic material such as resin or aluminum alloy.

Pistons 31 are reciprocally mounted in the respective cylinder holes 24, and the cylinder block 21 has six pistons 31. The piston 31 is made of a nonmagnetic material such as resin or aluminum alloy. The top of the piston 31 faces the adapter 26, and the bottom of the piston 31 faces the cam member 23. The pump chamber 32 is defined by the piston 31 and the magnet holder 28 of the adapter 26. When the piston 31 moves toward the adapter 26, the pump chamber 32 contracts, and when the piston 31 moves toward the cam member 23, the pump chamber 32 expands. Of the six pistons 31, two pistons 31 arranged coaxially form a pair.

A piston magnet 33 made of a permanent magnet is embedded in the top of each piston 31. The piston magnet 33 has an opposing surface that is exposed at the top of the piston 31 and faces the adapter 26. An adapter magnet 34 made of a permanent magnet is provided on the magnet holder 28. The adapter magnet 34 constitutes a magnetic force generating member, is embedded in the magnet holder 28, and has a facing surface that is exposed on the inner surface of the magnet holder 28 and faces the exposed surface of the piston magnet 33. As shown in FIGS. 6 and 8, the adapter magnet 34 has a rectangular bar shape and is arranged in parallel to the drive shaft 16. The shape of the adapter magnet 34 is not limited to a rectangular bar shape, and may be a cylindrical shape or an ellipse.

The facing surface of the adapter magnet 34 has the same polarity as the facing surface of the piston magnet 33. As a result, the adapter magnet 34 applies a magnetic force repelling the piston magnet 33 and applies a thrust force in the direction of expanding the pump chamber 32 to the piston 31.

As shown in FIGS. 6 and 8, the rotating body 35 is rotatably mounted on the bottom of each piston 31. The rotating body 35 is supported by a support pin 36 attached to the piston 31. As the rotating body 35, a ball bearing is used, and it has an inner annular member fixed to the support pin 36 and an outer annular member that is rotatably mounted on the outside via a large number of balls. .

The cam surface 37 is provided on the outer peripheral surface of the cam member 23, and the cam surface 37 is in rolling contact with the outer peripheral surface of the rotating body 35. As shown in FIG. 6, the cam surface 37 has two major axis portions with a maximum radius and two minor axis portions with a minimum radius, and has a shape such that the movement trajectory of the piston 31 becomes a sine curve. . When the cam member 23 is rotationally driven by the drive shaft 16, the piston 31 reciprocates between a position closest to the adapter 26 and a position farthest away from the adapter 26. As shown in FIG. 8, the drive shaft 16 is rotatably supported by a bearing 38 attached to the cylinder block 21.

In FIG. 6, two pistons 31 (a) and 31 (b), which are marked with parentheses a and b, are paired, and the rotating bodies of the two pistons 31 (a) and 31 (b) A state in which 35 is in rolling contact with the long diameter portion of the cam surface 37 is shown. At this time, the two pistons 31 (a) and 31 (b) are closest to the adapter 26. When the piston 31 moves toward the closest position, the two pistons 31 (a) and 31 (b) move toward the adapter 26 against the repulsive force between the piston magnet 33 and the adapter magnet 34. The pump chamber 32 is contracted.

When the cam member 23 is rotated 90 degrees from the position shown in FIG. 6, the short diameter portion of the cam surface 37 comes into rolling contact with the rotating body 35 of the two pistons 31 (a) and 31 (b). At this time, the two pistons 31 (a) and 31 (b) are furthest away from the adapter 26. When the cam member 23 rotates from the position where the long diameter portion of the cam surface 37 is in contact with the rotating body 35 to the position where the short diameter portion is in contact, the repulsive force between the piston magnet 33 and the adapter magnet 34 causes the piston 31 to be It moves to the position farthest from the position closest to 26. Thereby, the pump chamber 32 expands. The same applies to the other pairs of pistons 31.

Thus, under the state where the adapter magnet 34 applies a magnetic force in the direction in which the pump chamber 32 is expanded with respect to each piston 31, the rolling contact between the cam surface 37 of the cam member 23 and the rotating body 35 causes The piston 31 reciprocates linearly. That is, the cam member 23 and the piston 31 do not make sliding contact. As a result, wear of the cam surface 37 is prevented, and high durability of the compressor assembly 12 can be maintained even when the cam member 23 is rotated at a high speed.

Furthermore, since the paired pistons 31 move toward the outside at the same time or two at the same time toward the inside at the same time, the centers of gravity of the two pistons 31 that form a pair maintain a fixed position without being eccentric. Therefore, the dynamic balance of the six pistons 31 is increased, and it becomes possible to operate at high speed while suppressing the occurrence of vibration.

Since the central axes of all the cylinder holes 24 intersect at one point, all the pistons 31 can be driven by one cam member 23. Further, each piston 31 reciprocates in the direction perpendicular to the drive shaft 16. Accordingly, the dimension of the cylinder block 21 in the direction of the drive shaft 16 can be reduced. Thus, since a desired pump chamber volume can be obtained by the small cylinder block 21, the compressor 10a can be miniaturized.

Moreover, the electric motor 13 is an outer rotor type, and the thickness dimension of the electric motor 13 in the axial direction of the main shaft 14 is close to the thickness dimension of the cylinder block 21 as shown in FIG. The compressor assembly 12 is disposed on the outer side in the radial direction of the electric motor 13 and mounted on the surface side of the support plate 11, and the drive shaft 16 and the main shaft 14 are disposed in parallel to penetrate the support plate 11. The power transmission mechanism 19 is disposed on the back side of the support plate 11. Therefore, unlike the embodiment in which the drive shaft 16 and the main shaft 14 are arranged coaxially, in the present invention, since the axial dimension of the drive shaft 16 of the compressor 10a, that is, the thickness dimension is small, the compressor 10a is reduced in size and thickness. Can be

Furthermore, in the case where the main shaft 14 is connected coaxially to the drive shaft 16, in order to smoothly transmit the rotation of the main shaft 14 to the drive shaft 16, it is necessary to increase the assembly accuracy of both shafts. In contrast, in the present invention, by arranging the main shaft 14 and the drive shaft 16 in parallel, even if an error occurs in the parallelism of the main shaft 14 and the drive shaft 16, the error is absorbed by the timing belt 18. be able to. Thereby, it is not necessary to improve the assembly precision of the compressor assembly 12 and the electric motor 13, and the assembly workability | operativity of the compressor 10a can be improved. Further, by making the diameters of the drive pulley 15 and the driven pulley 17 different, it is possible to assemble various types of compressors 10a having different rotational speeds and rotational torques of the drive shaft 16 without changing the motor rotational speed. Instead of the timing belt 18 as a power transmission member, a V belt or a flat belt can be used, or a chain can be used. When a chain is used, a sprocket is used as a rotating body instead of the driving pulley 15 and the driven pulley 17.

When the drive shaft 16 is rotationally driven by the electric motor 13 and the pump chamber 32 is expanded by the piston 31, gas is supplied to the pump chamber 32 from the outside. On the other hand, when the pump chamber 32 is contracted by the piston 31, the gas in the pump chamber 32 is discharged to the outside. As shown in FIG. 8, a breathing hole 40 is provided in the cylinder block 21, and external air is supplied and discharged as the pump chamber 32 expands and contracts.

FIG. 10 (A) is an enlarged front view of the D portion in FIG. FIG. 10B is a side view showing the outer surface of the adapter 26 viewed from the direction of arrow E in FIG. FIG. 11A is a cross-sectional view taken along line FF in FIG. 10B and shows a cross section of the adapter 26. FIG. 11B is a cross-sectional view taken along the line GG in FIG. 11A and shows the inner surface of the magnet holder 28. 12A is a cross-sectional view taken along the line HH in FIG. 11B, and FIG. 12B is a cross-sectional view taken along the line II in FIG.

In FIG. 3, the adapter 26 (a) in which the symbol a is shown in parentheses faces the piston 31 (a) shown in FIGS. 6 and 8, and the adapter 26 ( b) faces the piston 31 (b).

As shown in FIG. 11A, an intake hole 41 and a discharge hole 42 communicating with the pump chamber 32 are provided in the magnet holder 28, respectively. The intake hole 41 communicates with an intake communication hole 43 provided in the flow path plate 29, and the discharge hole 42 communicates with a discharge communication hole 44 provided in the flow path plate 29. The intake communication hole 43 and the discharge communication hole 44 open on the attachment surface 45 of the flow path plate 29 as shown in FIG. The attachment surface 45 is attached in close contact with the surface of the support plate 11. As shown in FIGS. 4 and 7, the intake communication hole 43 communicates with the outside air through an intake port 46 provided in the support plate 11. The intake communication hole 43 communicating with the pump chamber 32 of the two pistons 31 (a) and 31 (b) forming the pair shown in FIG. 6 is connected to the flow path member 20 by an intake port 46 provided in the flow path member 20. It penetrates and communicates with the outside. The pump chamber 32 of the other piston 31 communicates directly with the outside through an intake port 46 provided in the support plate 11.

On the other hand, the discharge communication hole 44 penetrates the support plate 11 and communicates with the discharge hole 47 provided in the flow path member 20 as shown in FIG. Each discharge hole 47 communicates with a discharge flow path 48 provided in the flow path member 20, and the gas discharged from all the pump chambers 32 is supplied to the outside from a discharge port 49 of the discharge flow path 48. The A joint 50 communicating with the discharge port 49 is attached to the flow path member 20, and a pipe made of a hose or pipe (not shown) is attached to the joint 50. The gas discharged from each pump chamber 32 is supplied to the supply target member by piping.

As described above, since the gas discharged from all the pump chambers 32 is collected in one flow path member 20 and guided to the outside, it is not necessary to provide a plurality of pipes in the cylinder block 21, and the compressor 10a can be reduced in size.

As shown in FIG. 11 (A), a check valve 51 for intake is mounted in the intake hole 41, and a check valve 52 for discharge is mounted in the discharge hole 42. As shown in FIG. 11A, each

check valve

51, 52 has a base 53 attached to the magnet holder 28 and an elastic deformation portion 54 having a larger diameter than that of the base 53. The intake check valve 51 opens the intake hole 41 when the pump chamber 32 expands. As a result, outside air that is gas flowing in from the intake port 46 is supplied to the pump chamber 32. On the other hand, the check valve 51 closes the intake hole 41 when the pump chamber 32 contracts. On the other hand, the discharge check valve 52 closes the discharge hole 42 when the pump chamber 32 expands. On the other hand, when the pump chamber 32 contracts, the discharge check valve 52 opens the discharge hole 42. Thereby, the gas discharged from all the pump chambers 32 is discharged from the discharge port 49 to the outside.

The intake port 46 opens to the outside on the back side of the support plate 11, but an intake port that communicates with the intake hole 41 may be provided in the flow path plate 29. In that case, outside air is sucked into the pump chamber 32 from the surface side of the support plate 11.

13 is a front view showing a modified compressor assembly 12a, FIG. 14 is a cross-sectional view taken along line JJ in FIG. 13, and FIG. 15 is a perspective view of FIG. The compressor assembly 12a is mounted on the surface side of the support plate 11 in the same manner as the compressor assembly 12 described above, and the electric motor 13 is disposed on the surface side of the support plate 11 with the compressor assembly 12a positioned radially outward of the compressor assembly 12a. Installed. The rotational torque of the electric motor 13 is transmitted to the drive shaft 16 by the power transmission mechanism 19 disposed on the back side of the support plate 11 as in the case described above. The structure of the cylinder block 21 and the piston 31 incorporated therein is the same as that of the compressor assembly 12 shown in FIGS.

The compressor assembly 12 a has a cylinder block 21 in which six cylinder holes 24 are provided in the same manner as the compressor assembly 12 described above. The adapter 26a is mounted on the six mounting surfaces 25, and a solenoid 55 as a magnetic force generating member is provided on the adapter 26a. The solenoid 55 has a bobbin 57 in which an iron core 56 is incorporated, and a coil 58 is wound around the outside of the bobbin 57. As shown in FIG. 14, the connection terminal 59 of the coil 58 protrudes to the outside of the adapter 26 a, and power is supplied to the coil 58 from the outside via a power supply plug (not shown) connected to the connection terminal 59.

In the piston type compressor having the compressor assembly 12a shown in FIGS. 13 to 15, electric power is supplied to the coil 58, and the solenoid 55 generates a magnetic force repelling the piston magnet 33. As a result, thrust in the direction of expanding the pump chamber 32 is applied to the plurality of pistons 31. In this compressor assembly 12a, by controlling the amount of electric power to the coil 58 and the energization timing, the rotational force position of the cam member 23 determines the strength of the repulsive force applied to the piston magnet 33 by the solenoid 55 and the timing for generating the magnetic force. It can be changed according to.

The adapter 26 described above is formed by the magnet holder 28 and the flow path plate 29, whereas the adapter 26a has a block material into which the solenoid 55 is incorporated. The block member is provided with the intake holes 41 and the discharge holes 42 shown in FIGS. 10 to 12. Air is supplied from the outside to the pump chamber 32, and the compressed gas flows into the flow path member 20. It is discharged from the discharge port 49 to the outside.

16 to 23 show a piston type compressor 10b according to another embodiment. The compressor 10b has first and second compressor assemblies 12b, whereas the above-described compressor 10a has a single compressor assembly 12. Both compressor assemblies 12 b are mounted on the surface of the support plate 11 and are driven by an electric motor 13 mounted on the surface of the support plate 11. Similar to the compressor assembly 12, a driving pulley 15 as a driving side rotating body is mounted on the main shaft 14 of the electric motor 13, and a driven pulley 17 as a driven side rotating body is mounted on both driving shafts 16. The timing belt 18 as a power transmission member is stretched between a driving pulley 15 on the driving side and two driven pulleys 17 on the driven side. The driving pulley 15, the driven pulley 17, and the timing belt 18 form a power transmission mechanism 19. Composed. The power transmission mechanism 19 is disposed on the back side of the support plate 11, and the flow path member 20 is mounted on the back surface of the support plate 11. In the compressor 10b shown in FIGS. 16 to 23, the duplicate description of the same members as those constituting the compressor 10a described above is omitted.

As shown in FIGS. 21 and 23, the two compressor assemblies 12b have the same structure. A cylinder hole 24 communicating with the cam housing chamber 22 is provided in each cylinder block 21, and the cylinder hole 24 is provided in the cylinder block 21 every 120 degrees in a direction along the outer peripheral surface of the cylinder block 21. As with the compressor assembly 12 described above, the cylinder hole 24 communicates with the cam housing chamber 22 at the inner end and opens to the outer peripheral surface of the cylinder block 21 at the outer end. One piston 31 in both compressor assemblies 12b is arranged in a straight line as indicated by reference numerals 31 (a) and 31 (b).

The cylinder block 21 has three mounting surfaces 25, and the outer end of the cylinder hole 24 is open to the mounting surface 25. Adapters 26 are mounted on the respective mounting surfaces 25. Each adapter 26 has the same structure as that shown in FIGS. 10 to 12, and the piston 31 has the same structure.

As shown in FIGS. 19 and 22, an intake port 46 is provided in the support plate 11, and each intake port 46 communicates with the intake hole 41 via an intake communication hole 43 provided in the adapter 26. . Discharge holes 47 are provided in the flow path member 20, and the discharge holes 47 communicate with the discharge holes 42 via discharge communication holes 44 provided in the adapter 26, and discharge flow paths provided in the flow path member 20. 48. As shown in FIG. 21, a recessed groove 61 is provided between the mounting surfaces 25 adjacent in the direction along the outer peripheral surface, and the heat dissipation of the cylinder block 21 is enhanced.

When the electric motor 13 is driven, the respective cam members 23 are rotationally driven by both the drive shafts 16 via the timing belt 18. When the cam member 23 is rotationally driven, the piston 31 contracts the pump chamber 32 against the repulsive force of the adapter magnet 34 and the piston magnet 33. Thereby, the gas in the pump chamber 32 passes through the check valve 52 and flows into the discharge flow path 48 of the flow path member 20 through the flow path in the adapter 26. All the gas discharged from the six pump chambers 32 flows into the discharge flow path 48. The gas flowing into the discharge channel 48 is supplied from the discharge port 49 to an external supply target member.

In the compressor assembly 12b, an adapter magnet 34 is used as a magnetic force generating member. However, as with the compressor assembly 12a shown in FIGS. 13 to 15, when the solenoid 55 is provided in the adapter instead of the adapter magnet 34, The compressor assembly is configured such that the magnetic force generating member is a solenoid.

The present invention is not limited to the embodiment described above, and various modifications can be made without departing from the scope of the invention. For example, in the above-described

piston compressors

10a and 10b, it is used to compress air and supply it to the supplied member, but to compress other gas such as nitrogen gas and supply it to the supplied member. Each compressor can be applied.

The compressor of the present invention is applied to a fluid control system for supplying compression equipment to fluid equipment.

Claims

A compressor assembly having a cylinder block provided with a plurality of pistons for expanding and contracting the pump chamber, an adapter provided with an intake communication hole and a discharge communication hole communicating with the pump chamber, and a drive shaft for driving the piston A piston-type compressor comprising:
A main plate of the electric motor that drives the drive shaft and the drive shaft, and a support plate on which the compressor assembly and the electric motor are mounted on the surface side;
A power transmission mechanism disposed on the back side of the support plate and transmitting the rotation of the main shaft to the drive shaft;
A flow path member that is attached to the back surface of the support plate, communicates with the discharge communication hole, and guides the gas discharged from each pump chamber to the outside;
A piston compressor.
The piston type compressor according to claim 1, wherein
A cam member disposed in a cam housing chamber provided in the cylinder block and driven to rotate by the drive shaft;
A rotating body that is provided on the piston and rolls into contact with the cam surface of the cam member to apply a thrust in a direction in which the pump chamber contracts to the piston;
A piston magnet is provided on each piston,
A piston type compressor in which each adapter is provided with a magnetic force generating member that applies a thrust force in a direction in which the pump chamber expands to the piston by applying a magnetic force repelling the piston magnet.
3. The piston compressor according to claim 2, wherein the magnetic force generating member is an adapter magnet or a solenoid.
The piston compressor according to any one of claims 1 to 3, wherein the compressor assembly includes a cylinder block provided with six cylinder holes.
The piston type compressor according to any one of claims 1 to 3, comprising two compressor assemblies each having a cylinder block provided with three cylinder holes.
The piston type compressor according to any one of claims 1 to 5, wherein the power transmission mechanism includes a driving side rotating body fixed to the main shaft, a driven side rotating body fixed to the driving shaft, A piston-type compressor comprising a drive-side rotator and a power transmission member spanned between the driven-side rotator.