JPH0444864Y2 - - Google Patents

Description

[Detailed description of the invention] [Industrial application field] The present invention is a disc cam type reciprocating compressor. In a compressor that is installed to obtain a compression effect by making two reciprocating movements in one revolution of Regarding.

[Conventional technology]

Generally, in a disk cam type compressor, a cam chamber 5 is provided in the housing 1 (or cylinder block), and a pair of cylinder bores 4 in the front and rear are aligned parallel to the rotating shaft 3, as shown in the drawing of FIG. The holes are drilled at regular intervals. The cam chamber 5 is rotatably provided with a disc cam 13 which is mounted on the rotating shaft 3 and curved in the shape of a corrugated plate, while a double-headed piston is inserted through the cam chamber 5 into each cylinder bore 4. 8 is inserted so that it can move forward and backward. And again,
A cylindrical or cylindrical roller 14 is moored between the rear part of the piston 8 and the disk cam 13, and the rotation of the disk cam 13 can be transmitted to each piston 8 as reciprocating motion through the sliding rotation of the roller. It will be set up as possible. (Utility Model Publication No. 114184, JP-A-57-114184, JP-A-57-114184)
(Publication No. 110783) [Problems to be solved by the invention] However, in the disk cam type compressor of the conventional structure as described above, the inner wavy curved surfaces 13' formed on the front and rear sides of the disk cam 13 Circumferential side (rotating shaft 3
The wavy curved surface 13' of the cam 13 is caused by the fact that the radius of curvature is slightly different between the side (side) and the outer peripheral side, that is, the cylindrical or cylindrical roller 14 is disposed orthogonally to the rotating shaft 3 and brought into contact with the cam. Due to the characteristic shape of the disk cam, the radius of curvature on the inner circumferential side is slightly smaller than the radius of curvature on the outer circumferential side, and the contact stress on the rollers is higher on the inner circumferential side than on the outer circumferential side. On the sliding surface, a larger sliding rotation occurs on the inner peripheral side than on the outer peripheral side, and this sliding rotation causes problems such as premature wear and peeling on the sliding contact surface between the disc cam and the roller. There are problems with this. Incidentally, it is possible to temporarily solve the above-mentioned problem by shifting the sliding contact position of the roller against the disc cam in the outer circumferential direction to reduce the difference in the radius of curvature. By shifting in the outer circumferential direction, the outer diameter of the disc cam becomes larger, which brings about a new problem in that the body diameter of the compressor itself becomes larger.

The present invention is an attempt to improve the above-mentioned problems, and in the mooring part of the rollers formed between the disc cam and the double-ended piston, the rollers on the inner peripheral side of the disc cam are The problem to be solved is to prevent early wear and peeling on the inner peripheral side by reducing the amount of sliding rotation as much as possible. That is,
The present invention allows the roller to slide and rotate in response to the difference in the radius of curvature between the outer and inner circumferential sides of the wavy curved surface formed on the disk cam at the mooring part of the roller formed between the disk cam and the double-ended piston. It is characterized by solving the above-mentioned problems by making it possible to perform the following tasks, and its specific means and effects are as follows.

[Means for solving problems]

Inside the cylinder block, multiple sets of cylinder bores are bored parallel to the axis of rotation, facing each other on the front and rear sides to form a pair of front and rear cylinders, with a cam chamber in between, and each cylinder bore is equipped with a double-headed piston. A disc cam fixed to the rotating shaft and curved into a corrugated plate shape is rotatably installed in the cam chamber, and a cylinder or cylinder is inserted between the disc cam and the double-ended piston. In a disk cam type compressor formed by mooring shaped rollers, the rollers are divided into a plurality of rollers. Each roller is interposed in series between the disk cam and the double-headed piston along the radial direction of the disk cam, so that each roller can be slid and rotated independently.

[Effect]

Because a plurality of divided rollers are moored between the disc cam and the double-ended piston, each roller slides independently in response to the difference in the radius of curvature between the outer and inner peripheries of the disc cam. By rotating, the amount of sliding rotation of the roller on the inner peripheral side of the disc cam can be reduced. That is, early wear and peeling on the inner peripheral side of the disc cam can be prevented.

〔Example〕

Hereinafter, specific embodiments of the present invention will be described with reference to the illustrative drawings.

FIG. 1 is a drawing showing a first embodiment,
In the drawing, 1 is a housing forming the outer shell of the compressor, and 16 is a cylinder block. The cylinder block 16 is composed of a front cylinder block 16F and a rear cylinder block 16R, and both cylinder blocks 16F and 16R are provided with bearing portions 2F and 2R located at the center thereof. A rotating shaft 3 is rotatably supported on 2F and 2R. One end of the rotating shaft 3 passes through a front housing 1F (described later) and is connected to an electromagnetic clutch (not shown), and is connected to an engine (not shown) through connection and disconnection of the electromagnetic clutch.
The driving force of the rotary shaft 3 can be transmitted to the rotary shaft 3. Also, both cylinder blocks 16F,
16R has multiple cylinder bores 4 connected to the rotating shaft 3.
The hole is drilled parallel to the That is, they are arranged at regular intervals on the same circumference so as to surround the rotating shaft 3. Each cylinder bore 4 is divided into a front side and a rear side so as to form a front and rear pair with a cam chamber 5 in between.
There is a compression chamber 7 between the two and a double-headed piston 8 is fitted therein so that it can move forward and backward.

Further, in the housing 1 described above, 1F is a front housing that covers the open end of the front cylinder block 16F with the front valve plate 6F in between, and 1R is the front housing that covers the open end of the front cylinder block 16F with the front valve plate 6R in between.
A rear housing that covers an open end of R,
Both housings 1F, 1R have suction chambers 9F, 9R and a discharge chamber 10 corresponding to each cylinder bore 4.
F, 10R are provided with an annular partition between them. The front valve plate 6F and rear valve plate 6R have suction ports corresponding to the suction chambers 9F and 9R, and discharge chambers 10F and 10R.
The discharge ports are respectively opened correspondingly. Also, at the suction port, a suction valve 11 is located on the compression chamber 7 side.
F, 11R are provided so as to be able to open and close freely through the suction stroke of the double-headed piston 8, and discharge valves 12F, 12 are located at the discharge port on the side of the discharge chambers 10F, 10R.
R is provided so as to be able to open and close freely through the compression stroke of the double-headed piston 8.

On the other hand, a disk cam 13 is fixed to the rotating shaft 3 and rotatably provided in the cam chamber 5. The disk cam 13 is formed by curving both its front and rear surfaces in the circumferential direction into a corrugated plate shape (hereinafter referred to as "wavy curved surface 13'"). A cylindrical roller 14 is moored between the disc cam 13 and the double-headed piston 8 so that it can freely rotate with its rotation center (center line) extending in the radial direction of the disc cam 13. 13 can be transmitted to each double-headed piston 8 as reciprocating motion. More specifically, the roller 14 is divided into rollers 14a and 14b, and both rollers 14a and 14b are capable of contacting the wavy curved surface 13' and the sliding member 15 fitted to the rear surface of the double-headed piston 8, respectively. provided. That is, each of the rollers 14a, 14b is provided so as to be able to independently rotate at a circumferential speed corresponding to the radius of curvature of the wavy curved surface 13'.

FIG. 2 is a drawing showing a second embodiment,
In the first embodiment, each roller 14a, 14b
is formed in a cylindrical shape, whereas in this embodiment it is formed in a cylindrical shape with a hollow portion 14'.
Further, FIGS. 3 and 4 are applied examples of the above-mentioned two embodiments, and in both the above-mentioned embodiments, a sliding member 15 is fitted to the rear part of the double-headed piston 8, and the sliding member 15 is The rollers 14a, 14b are provided so as to be in contact with each other, whereas in both application examples, the rollers 14a, 14b are provided so as to be in direct contact with the rear portion of the double-headed piston 8. Furthermore, in each of the above embodiments, the roller 14
Although it is divided into two into rollers 14a and 14b, it is also possible to divide it into three or more. Although not shown in the drawings, the rollers 14 can be divided into a combination of hollow rollers and cylindrical rollers, or the divided rollers can be formed with slightly different diameters. It is also possible to coat the outer circumferential surface of the divided rollers with a soft material, thereby providing a noise prevention effect on the outer circumferential divided rollers and an abrasion and peeling prevention effect on the inner divided rollers. can be further enhanced.

Next, a first embodiment, whose operation is shown in FIG. 1, will be described.

By transmitting the driving force of the engine to the rotating shaft 3 through the connection operation of an electromagnetic clutch (not shown),
A state in which the disc cam 13 rotates in the cam chamber 5 is obtained. A roller 14 is moored between the disc cam 13 and the double-ended piston 8 by contacting the wavy curved surface 13' and the sliding member 15, so that the disc cam 13 rotates through the sliding rotation of the roller 14. This is transmitted to the double-headed piston 8, and a state is obtained in which each double-headed piston 8 continuously reciprocates within each cylinder bore 4. However, the roller 14 is divided into a plurality of rollers 14a and 14b. Accordingly, the wavy curved surface 1 formed on the disc cam 13
It is possible to obtain a state in which the circumferential speeds corresponding to the difference in the radius of curvature between the outer circumferential side and the inner circumferential side of 3' correspond to the difference, and the respective parts rotate independently. That is, it is possible to reduce the slippage of the roller 14b that abuts the inner circumferential side of the wavy curved surface 13', thereby reducing early wear on the inner circumferential side of the roller 14b and the wavy curved surface 13' that abuts the roller 14b. And the effect of inhibiting peeling can be obtained.

[Effect of idea]

The present invention is constructed as described above.
As mentioned above, the roller moored between the disc cam and the double-ended piston is divided into multiple rollers, and each roller is made independent by corresponding to the difference in the radius of curvature on the outer and inner periphery of the disc cam. By making it possible to rotate the disc cam, it has become possible to reduce the amount of slippage of each roller on the sliding surface between the disc cam and the roller, thereby preventing early wear and peeling of the disc cam and the disc cam. We have now been able to effectively prevent this.

In addition, in the present invention, the roller is divided into a plurality of rollers as described above, and each roller can be slid and rotated with an independent circumferential speed, so that each roller becomes a disc. It became possible to rub the cam closer to the inner circumference on the wavy curved surface of the cam, and as a result, the diameter of the disk cam and cylinder block could be reduced by that amount. In other words, it has become possible to downsize the overall shape of the compressor.

In addition, by forming the rollers into a hollow cylindrical shape as shown in the second embodiment, it is possible to reduce the weight accordingly, and also to reduce the mass of the reciprocating portion of the double-headed piston. This makes it possible to reduce the range of torque fluctuation in the mooring section. Furthermore, the heat dissipation effect of frictional heat generated during operation can be enhanced.

[Brief explanation of the drawing]

FIG. 1 is a drawing showing a first embodiment,
Vertical sectional view showing the entire disc cam compressor, No. 2
The figure is a drawing showing the second embodiment, and is also a vertical cross-sectional view showing the entire disc cam type compressor.
The figure is a drawing showing an applied example of the first embodiment, and is a longitudinal sectional view showing the entire disc cam type compressor, and FIG. 4 is a drawing showing an applied example of the second embodiment. FIG. 1 is a longitudinal sectional view showing the entire disc cam type compressor. Further, FIG. 5 is a diagram showing a conventional structure, and is a longitudinal sectional view showing the entire disk cam type compressor. 1... Housing, 1F... Front housing, 1R... Rear housing, 2F, 2R... Bearing section, 3... Rotating shaft, 4... Cylinder bore,
5...Cam chamber, 6F, 6R...Valve plate,
7...Compression chamber, 8...Double-ended piston, 9F, 9R
...Suction chamber, 10F, 10R...Discharge chamber, 11
F, 11R... Suction valve, 12F, 12R... Discharge valve, 13... Disc cam, 13'... Wavy curved surface,
14...Koro, 14a, 14b...Koro, 14'
...Hollow part, 15...Sliding member, 16...Cylinder block, 16F...Front cylinder block, 16R...Rear cylinder block.

Claims (1)

[Scope of utility model registration request] Inside the cylinder block, multiple sets of cylinder bores are bored parallel to the axis of rotation, facing each other on the front and rear sides to form a pair of front and rear cylinders, with a cam chamber in between, and each cylinder bore is equipped with a double-headed piston. A disc cam fixed to the rotating shaft and curved in the shape of a corrugated plate is rotatably installed in the cam chamber, and a roller is moored between the disc cam and the double-ended piston. The disc cam type reciprocating compressor consists of a disc cam type reciprocating compressor in which the above-mentioned roller is divided into a plurality of parts, and each roller is interposed in series between the disc cam and the double-ended piston along the radial direction of the disc cam. Mooring structure of rollers in a reciprocating compressor.