JPH0861236A - Reciprocating compressor - Google Patents

Abstract

PURPOSE: To improve durability of a reciprocating compressor and its life by suppressing temperature rise of a valve plate to be fixed to a cylinder. CONSTITUTION: A packing 31 as a seal member is composed of a circular part 31E having a large diameter 31A at an inner peripheral side, and formed with a cutout 31B and an escape hole 31C, and substantially U-shaped projections 31F each projected from an outer peripheral side of the circular part 31E outwardly in a diameter direction, and formed with a bolt through-hole 31D. When the packing 31 is superposed on a valve plate 18 as indicated by one-dotted line, a large heat raddiation surface 32 can be secured in the vicinity of an outer surface 18A of the valve plate 18. A part of compression heat can be radiated by the heat radiation surface 32.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reciprocating compressor suitable for compressing a fluid such as air.

[0002]

2. Description of the Related Art FIGS. 4 to 6 show an air compressor as an example of a reciprocating compressor according to the prior art.

In the drawing, reference numeral 1 denotes an electric motor as a drive source, and the electric motor 1 is roughly composed of a stator 2, a motor housing 3, a rotating shaft 5, a rotor 8 and the like, which will be described later.

Reference numeral 2 denotes a stator which constitutes a part of the electric motor 1. The stator 2 is composed of a stator coil and the like, and surrounds the rotor 8 from the outer peripheral side. And
The stator 2 constitutes a part of the motor housing 3 and is integrally fixed to a crankcase 9 described later.

Reference numeral 3 indicates a motor housing of the electric motor 1. The motor housing 3 is provided on the stator 2, a lid 4 provided on the base end side of the stator 2, and a tip end side of the stator 2. It is composed of a cylindrical portion 9D described later. The lid 4 of the motor housing 3 and the like are integrally fixed to a partition wall 9B of a crankcase 9 described later via long through bolts (not shown) and the like.

Reference numeral 5 denotes a rotating shaft of the electric motor 1. The rotating shaft 5 has its base end side pivotally supported by a bearing 6 provided at the center of the lid 4, and its tip end side at the center of the partition wall 9B of the crankcase 9. The bearing 7 is axially supported. Then, the tip end side of the rotary shaft 5 becomes an output shaft portion 5A protruding into the crankcase 9, and the output shaft portion 5A constitutes a part of a crankshaft 11 described later.

Reference numeral 8 denotes a rotor provided integrally with the rotary shaft 5 in the motor housing 3, and the rotor 8 is made of a permanent magnet or the like and faces the stator 2 in the radial direction. Then, the rotor 8 rotationally drives the rotating shaft 5 by the electromagnetic force acting on the rotor 8.

Reference numeral 9 denotes a box-shaped crankcase. The crankcase 9 has an open end 9A on the front end side and a body portion 9C closed on the base end side by a partition wall 9B.
And a tubular portion 9D which projects from the base end side of the body portion 9C toward the stator 2 and constitutes the motor housing 3 together with the stator 2 and the like.

Reference numeral 10 denotes a cover attached to the open end 9A of the crankcase 9. The cover 10 is formed in a cylindrical shape with a lid and defines a crank chamber A in the crankcase 9. Further, the cover 10 has a plurality of vent holes 10A, 1
0A is bored, and each of the ventilation holes 10A has a suction filter 10
Air is sucked into the crank chamber A via B.

Reference numeral 11 denotes a crank shaft rotatably provided in the crank case 9, and the crank shaft 11 includes an output shaft portion 5A of the rotary shaft 5 protruding into the crank case 9, and the crank shaft is provided. Balance weight 1 for 11
2 are integrally formed.

Reference numeral 13 denotes a cylinder mounted on the crankcase 9. The cylinder 13 is integrally formed with a cylindrical portion 13A into which a piston 14 described later is slidably fitted and an upper end side of the cylindrical portion 13A. , A mounting portion 13B having a substantially square shape to which a cylinder head 23 and the like described later are mounted.

Reference numeral 14 denotes a piston slidably fitted in the cylinder 13, and a piston ring 14A and a rider ring 14B are attached to the piston 14, and the piston 14 has the piston ring 14A and the rider ring 14B interposed therebetween. Slidingly contacts the inner peripheral surface of the cylindrical portion 13A of the cylinder 13. The piston 14 is provided with a piston pin 15, and the piston pin 15 is connected to the crankshaft 11 via a connecting rod 16 described later.

Reference numeral 16 designates the rotation of the crankshaft 11 and the piston 1
4 is a connecting rod that is converted into reciprocating motion, and the connecting rod 16 is rotatably connected to the crankshaft 11 on the large end 16A side,
The small end 16B side is provided with the piston pin 15 on the piston 14.
Is rotatably connected via.

Reference numeral 17 denotes a packing as a seal member provided on the mounting portion 13B of the cylinder 13, and the packing 17 is formed as a thin plate having a substantially square shape with an elastic resin material as shown in FIG. A large-diameter hole 17A corresponding to the inner diameter of the cylinder 13 is bored therethrough.
Further, a notch 17B for a suction valve 21 described later is formed on one side of the large diameter hole 17A, and a relief hole 1 for a fixing screw 21A described below is slightly separated from the large diameter hole 17A on the other side.
7C is formed in an oval shape. Further, the packing 17 has bolt insertion holes 17 located at respective corners.
D, 17D, ... Are drilled.

Reference numeral 18 denotes a valve plate which is airtightly fixed to the mounting portion 13B of the cylinder 13 via a packing 17, and the valve plate 18 is formed of a highly rigid metal material or the like as a substantially square flat plate, and the piston A compression chamber B is defined in the cylinder 13 with respect to the cylinder 14. Here, the valve plate 18 has four outer surface portions 18A, 18A, ... And bolt insertion holes 18B, 18B ,. And
Bolts (not shown) are inserted into the bolt insertion holes 18B together with the bolt insertion holes 17D of the packing 17, and the bolts are screwed into the cylinder head 23 described later on the cylinder 13 via the valve plate 18 and the like. I'm wearing it. Further, as shown in FIG. 6, a discharge hole 19 for a discharge valve 26 and a suction hole 20 for a suction valve 21 which will be described later are formed in the valve plate 18,
The suction hole 20 and the discharge hole 19 connect the inside of the compression chamber B to the inside of a suction chamber C and a discharge chamber D described later.

Reference numeral 21 denotes a suction valve that opens and closes the suction hole 20 of the valve plate 18. The suction valve 21 is formed in a long flat plate shape by an elastic spring material or the like, and one end of the suction valve 21 has the fixing screw 2
It is fixed to the lower surface of the valve plate 18 by 1A and 21A. The other end side of the suction valve 21 becomes a free end, and is separated from and seated on the lower surface of the valve plate 18 in response to the reciprocating movement of the piston 14, thereby separating the inside of the compression chamber B and the suction chamber C from the suction hole 2
Connect and disconnect via 0.

Reference numeral 22 denotes a head packing interposed between the valve plate 18 and the cylinder head 23. The head packing 22 hermetically seals the space between the valve plate 18 and the cylinder head 23.

Reference numeral 23 denotes a cylinder head mounted on the cylinder 13 via a valve plate 18, a head packing 22, etc., the cylinder head 23 has a partition wall 23A, and the partition wall 23A has a suction chamber inside the cylinder head 23. It is divided into C and discharge chamber D. Further, the cylinder head 23 is provided with a suction port 23B and a discharge port 23C, and the suction port 23B communicates with the crank chamber A via a suction pipe 24.

Reference numeral 25 denotes an unload valve located above the suction hole 20 and attached to the cylinder head 23. The unload valve 25 pushes the suction valve 21 at its tip when the compressor is started. However, the compressor is unloaded by keeping the suction valve 21 open.

Reference numeral 26 denotes a discharge valve provided on the upper side surface of the valve plate 18. The discharge valve 26 opens and closes the discharge hole 19 in accordance with the reciprocating movement of the piston 14, and the discharge hole 19 is formed in the compression chamber B. The discharge chamber D is communicated with and cut off via the discharge chamber D.

The reciprocating air compressor according to the prior art has the above-mentioned structure, and its operation will be described below.

First, when the rotating shaft 5 is rotationally driven by the electric motor 1, the crankshaft 11 is rotationally driven together with the output shaft portion 5A of the rotating shaft 5. The rotation of the crankshaft 11 is converted into the reciprocating motion of the piston 14 via the connecting rod 16, and the piston 14 reciprocates in the cylinder 13 so as to repeat the suction stroke and the discharge stroke.

Here, the suction chamber C in the crankcase 23
Communicates with the inside of the crank chamber A through the suction pipe 24, and in the suction stroke of the piston 14, from the crank chamber A to the suction chamber C.
Air is sucked into the compression chamber B while flowing inward in the direction of the arrow E. Also, the discharge stroke of the piston 14 (compression stroke)
Then, the piston 14 compresses the air in the compression chamber B to open the discharge valve 26, and the compressed air is discharged from the compression chamber B to the discharge chamber D. The compressed air is stored in an external air tank (not shown) or the like via the discharge port 23C of the cylinder head 23.

[0024]

In the air compressor according to the above-mentioned conventional technique, the air sucked into the compression chamber B from the suction hole 20 of the valve plate 18 is transferred to the cylinder 13 (compression chamber B).
Since the piston 14 is compressed by the reciprocating motion inside the cylinder 13, compression heat is generated in the compression chamber B in the cylinder 13, and this compression heat is transmitted to the cylinder 13, the valve plate 18, etc., and these cylinder 13 and the valve The heat is gradually radiated to the outside from the plate 18 or the like.

However, since the valve plate 18 is sandwiched between the packing 17 and the head packing 22 and the heat radiation area to the outside is very small even if the temperature rises, the compression heat at this time is transmitted to the cylinder 13 As a result, the temperature of No. 13 is greatly increased.

As a result, the piston 14 receives the heat from the cylinder 13 and quickly rises in temperature, causing a problem that the piston ring 14A, the rider ring 14B, etc. of the piston 14 are prematurely unevenly worn. Further, at this time, heat from the piston 14 is transferred to the small end portion 16B of the connecting rod 16 via the piston pin 15 and the bearing 16C provided between the two.
(See FIG. 5) has a problem that the life is shortened due to seizure or the like.

Further, the heat of the compressed air discharged into the discharge chamber D through the discharge valve 26 and the like is transmitted to the upper side surface of the valve plate 18, the inner surface of the cylinder head 23, etc., so that the temperature of the entire cylinder head 23 rises. become. Then, the heat from the valve plate 18 and the cylinder head 23 is transferred from the discharge chamber D side to the suction chamber C side, and the entire inside of the suction chamber C becomes a high temperature state. Therefore, the air in the suction chamber C is sucked into the compression chamber B. Temperature rises, the piston 1
There is a problem that 4 etc. are exposed to a high temperature state.

The present invention has been made in view of the above-mentioned problems of the prior art. In the present invention, the heat of compression when air or the like is compressed in the compression chamber is transmitted to the valve plate, so that the temperature of the valve plate or the like rises. It is an object of the present invention to provide a reciprocating compressor which can be effectively prevented and whose durability and life can be surely improved.

[0029]

In order to solve the above-mentioned problems, the invention described in claim 1 is a crankcase in which a crankshaft is rotatably provided, and a cylinder mounted on the crankcase, A piston that is inserted into the cylinder and reciprocates in the cylinder by being driven by the crankshaft, and is fixed on the cylinder so as to define a compression chamber in the cylinder between the piston and the piston. And a seal member that is provided between the valve plate and the cylinder and seals between the valve plate and the cylinder, the seal member increasing the heat dissipation area of the valve plate. The structure adopted is smaller than the valve plate.

According to a second aspect of the present invention, a crankcase in which a crankshaft is rotatably provided, a cylinder mounted on the crankcase, and the cylinder is inserted into the cylinder and driven by the crankshaft. Of the piston that reciprocates in the cylinder by being driven, a valve plate fixed on the cylinder so as to define a compression chamber in the cylinder between the piston, and the valve plate and the cylinder. A heat insulating part which is provided between the valve plate and the cylinder, and which seals between the valve plate and the cylinder, and which blocks heat from the compression chamber to the valve plate on the side of the compression chamber of the valve plate. Is adopted.

[0031]

With the above construction, in the invention described in claim 1,
Since the seal member is formed smaller than the valve plate and the heat dissipation area of the valve plate is large, the temperature rise of the valve plate can be surely suppressed and, for example, a cylinder head mounted on the valve plate, etc. The temperature rise can be suppressed, and the temperature of the air sucked into the compression chamber can be lowered to prevent the temperature rise of the entire compressor.

Further, according to the second aspect of the present invention, since the heat insulating portion is provided between the valve plate and the compression chamber so as to block the heat from the compression chamber from being transferred to the valve plate. ,
It is possible to reliably suppress the temperature rise of the valve plate, cylinder head, etc., and lower the temperature of air etc. sucked into the compression chamber,
It is possible to prevent the temperature of the entire compressor from rising.

[0033]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment of the present invention will be described below with reference to FIGS. In the embodiment, the same components as those of the conventional technique shown in FIGS. 4 to 6 are designated by the same reference numerals and the description thereof will be omitted.

FIG. 1 shows a first embodiment of the present invention.

In the figure, 31 is a mounting portion 13B of the cylinder 13.
A packing as a sealing member provided between the valve plate 18 and the valve plate 18 is shown. The packing 31 is the packing 1 described in the related art.
Large hole 31A, notch 3 for suction valve 21 almost the same as 7
1B, a relief hole 31C for the fixing screw 21A, and bolt insertion holes 31D, 31D, ... Are formed.

However, as shown in the drawing, the packing 31 has an annular portion 31E which is formed in an annular shape so as to surround the periphery of the large diameter hole 31A, and 4 which projects radially outward from the outer peripheral side of the annular portion 31E. .., and the surface area thereof is smaller than that of the valve plate 18. Each of the protrusions 31F of the packing 31 has a substantially U shape, and each of the protrusions 31F has a corresponding bolt insertion hole 31.
D is formed.

The reciprocating air compressor according to the present embodiment has the above-mentioned structure, and its basic operation is not different from that of the prior art.

Therefore, in this embodiment, the packing 31 is
An inner peripheral side has a large diameter hole 31A, an annular portion 31E having a notch 31B and a relief hole 31C, and the annular portion 31.
It projects radially from the outer peripheral side of E and each bolt insertion hole 31D
Since it is composed of substantially U-shaped protrusions 31F, 31F, ... In which the packing 31 is overlapped with the valve plate 18 as shown by the alternate long and short dash line in FIG.
A large heat dissipation surface 32 can be secured in the vicinity of each outer surface portion 18A of 8, and a part of the compression heat can be dissipated to the outside by this heat dissipation surface 32.

That is, when the valve plate 18 is fixed on the mounting portion 13B of the cylinder 13 via the packing 31, the valve plate 18 is positioned outside the annular portion 31E of the packing 31 and is attached to the mounting portion 13B of the cylinder 13 and the valve. A minute gap is formed between the plate 18 and the heat dissipation surface 32, and the heat dissipation surface 32 is kept in contact with the outside air through this gap. Then, when the heat from the compressed air compressed in the compression chamber B by the reciprocating motion of the piston 14 is transmitted to the valve plate 18, this heat is transferred to the heat radiating surface 3 of the valve plate 18.
It is possible to radiate heat to the outside from 2 and to reliably suppress the temperature rise of the valve plate 18.

Therefore, according to this embodiment, the heat dissipation area of the valve plate 18 can be expanded to improve the cooling efficiency, the temperature rise of the cylinder 13, the piston 14, etc. can be effectively reduced, and the compression The durability and life of the machine can be surely improved.

Next, FIG. 2 shows a second embodiment of the present invention, which is characterized by the packing 4 as a seal member.
1 is made of an elastic resin material or the like having a heat insulating property in a substantially square shape like the valve plate 18, and a suction valve 21 which is elongated in a central portion of the packing 41 to correspond to the shape of the suction valve 21.
This is because the valve hole 41A for the vehicle was formed.

Here, the packing 41 has a fixing screw 21
A relief hole 41B for A, a circular communication hole 41C communicating with the discharge hole 19 of the valve body 18, and bolt insertion holes 41D, 41D, ... Corresponding to each bolt insertion hole 18B of the valve plate 18 are provided. Has been done.

At the central portion of the packing 41, the inside of a circle 42 (corresponding to the inner diameter of the cylinder 13) shown by the chain double-dashed line in FIG. 2 becomes a heat insulating portion 41E, and the heat insulating portion 41E connects the packing 41 to the valve plate 18 By covering the side face of the compression chamber of the valve plate 18 when overlapped with the above, heat from the inside of the compression chamber B is prevented from being directly transferred to the valve plate 18.

Thus, in this embodiment having such a structure, when the valve plate 18 is fixed on the mounting portion 13B of the cylinder 13 via the packing 41, the heat insulating portion 41E of the packing 41 secures the valve plate 18 to the cylinder. 13 (compression chamber B), the heat from the compressed air compressed in the compression chamber B can be insulated from being transferred to the valve plate 18, and the temperature increase of the valve plate 18 can be effectively prevented. it can.

Next, FIG. 3 shows a third embodiment of the present invention. The feature of this embodiment is that a heat radiating plate and a heat insulating packing are provided between the packing used in the prior art and the valve plate. There is that.

In the figure, reference numeral 51 denotes a heat radiating plate which is inserted between the packing 17 and a heat insulating packing 52 which will be described later. The heat radiating plate 51 is formed of a metal material into a rectangular plate shape, and the packing 17 and the valve plate 18 are provided. Compared to the above, the length is formed in the left-right direction by the dimension L. And the heat sink 5
1 has a valve hole 51A for the suction valve 21 elongated in correspondence with the shape of the suction valve 21 and a relief hole 5 for the fixing screw 21A.
1B, a circular communication hole 51C communicating with the discharge hole 19 of the valve plate 18, and bolt insertion holes 51D, 51D, ... Corresponding to the bolt insertion hole 17D of the packing 17.

Here, in the central portion of the heat radiating plate 51, a portion located inside the large diameter hole 17A when the packing 17 is superposed serves as a contact surface portion 51E, and the contact surface portion 51E is compressed air from the compression chamber B. It directly contacts with and insulates the heat from the compressed air from being transmitted to the valve plate 18 side. The left and right sides of the heat radiating plate 51 become heat radiating parts 51F, 51F projecting from the packing 17, and the heat radiating parts 51F directly contact with the outside air, so that the heat transmitted from the compression chamber B to the heat radiating plate 51. To the outside.

Reference numeral 52 denotes a heat insulating packing which is interposed between the heat radiating plate 51 and the valve plate 18 and constitutes a sealing member together with the packing 17. The heat insulating packing 52 is the same as the packing 41 described in the second embodiment. A valve hole 52A for the suction valve 21 extending in a slender shape corresponding to the shape of the suction valve 21 of the valve plate 18, a relief hole 52B for the fixing screw 21A, and a discharge hole of the valve body 18 There are provided a communication hole 52C communicating with 19, a bolt insertion hole 52D, 52D, ... Corresponding to each bolt insertion hole 18B of the valve plate 18, and a heat insulating portion 52E. The heat insulating packing 52 is attached to the valve plate 18
A heat insulating portion that covers the side surface of the compression chamber.

Thus, also in the present embodiment having such a configuration, the heat radiation plate 51 and the valve plate 18 are disposed so that the heat radiation plate 51 and the heat insulating packing 52 are overlapped with each other, so that the heat radiation plate 51 comes into contact with each other. While the heat from the compression chamber B is received by the heat dissipation plate 51 at the surface portion 51E, this heat is dissipated from the heat dissipation portion 5 as well.
Heat can be radiated to the outside from 1F.

The heat insulating packing 52 is interposed between the heat radiating plate 51 and the valve plate 18, so that the heat from the compression chamber B is transferred to the valve plate 18 via the heat radiating plate 51.
The valve plate 18 can be reliably shut off by 2E or the like, and the temperature rise of the valve plate 18 due to heat from the compressed air can be effectively prevented.

Therefore, by preventing the temperature rise of the valve plate 18, it is possible to prevent the temperature rise of the suction chamber C and the like in the cylinder head 23, and also to reduce the temperature rise of the cylinder 13 and the temperature of the piston 14 and the like. By lowering, the durability and life of the compressor can be surely improved.

In each of the above embodiments, the reciprocating air compressor in which the piston 14 reciprocates in the cylinder 13 has been described as an example, but the present invention is not limited to this, and, for example, a rocking piston type. It may be applied to a reciprocating compressor, and is generally applicable to a reciprocating compressor that compresses a fluid other than air.

[0053]

As described in detail above, according to the first aspect of the invention, the seal member provided between the valve plate and the cylinder is formed smaller than the valve plate, and the heat radiation area of the valve plate is increased. The temperature rise of the valve plate can be surely suppressed and the valve plate can be kept in a relatively low temperature state, the temperature rise of the compressed fluid can be surely prevented, and the temperature rise of the piston can be prevented. It is possible to greatly improve the durability and life of the piston ring and the like.

Also, in the invention described in claim 2, since the heat insulating portion is provided between the valve plate and the compression chamber to block the heat from the compression chamber from being transferred to the valve plate, The temperature rise of the valve plate due to the heat of the valve plate can be suppressed, and the valve plate can be kept in a relatively low temperature state, the temperature increase of the compressed fluid can be reliably prevented, and the piston temperature increase can be prevented. It can greatly improve the durability and service life.

[Brief description of drawings]

FIG. 1 is a perspective view showing a valve plate and packing of an air compressor according to a first embodiment of the present invention.

FIG. 2 is a perspective view showing a valve plate and packing of an air compressor according to a second embodiment of the present invention.

FIG. 3 is a perspective view showing a valve plate and packing of an air compressor according to a third embodiment of the present invention.

FIG. 4 is a vertical cross-sectional view showing an air compressor according to the related art.

5 is a cross-sectional view showing an enlarged main part in FIG.

FIG. 6 is a perspective view showing a valve plate and packing according to the related art.

[Explanation of symbols]

 9 Crankcase 11 Crankshaft 13 Cylinder 14 Piston 17, 31, 41 Packing (seal member) 18 Valve plate 19 Discharge hole 20 Suction hole 21 Suction valve 23 Cylinder head 26 Discharge valve 32 Radiating surface 51 Radiating plate 52 Heat insulating packing (sealing member) ) A crank chamber B compression chamber

Claims (2)

[Claims] 1. A crankcase in which a crankshaft is rotatably provided, a cylinder mounted on the crankcase, a cylinder which is inserted into the cylinder and driven by the crankshaft to reciprocate in the cylinder. A moving piston, a valve plate fixed on the cylinder so as to define a compression chamber in the cylinder between the piston, and the valve plate provided between the valve plate and the cylinder. A reciprocating compressor having a seal member for sealing between the cylinder and the cylinder, the seal member being formed smaller than the valve plate so as to increase the heat radiation area of the valve plate. 2. A crankcase in which a crankshaft is rotatably provided, a cylinder mounted on the crankcase, a cylinder that is inserted into the cylinder, and is reciprocated in the cylinder by being driven by the crankshaft. A moving piston, a valve plate fixed on the cylinder so as to define a compression chamber in the cylinder between the piston, and the valve plate provided between the valve plate and the cylinder. A reciprocating compressor comprising: a seal member for sealing between the cylinder and a cylinder; and a heat insulating section for blocking transfer of heat from the compression chamber to the valve plate, provided on a side surface of the compression chamber of the valve plate. .