JPH0444865Y2 - - Google Patents

Description

[Detailed description of the invention] [Industrial application field] The present invention is a disc cam type reciprocating compressor. The present invention relates to an improvement of a roller portion moored between a disc cam and a double-headed piston in a compressor that is installed to obtain a compression effect by reciprocating twice in one revolution, that is, to a mooring structure of the rollers.

[Conventional technology]

In general, in a disk cam type compressor, as shown in FIGS. 7 and 9, a cam chamber 5 is provided in a cylinder block 1, and a pair of cylinder bores 4 in the front and rear are parallel to the rotation axis 3. The holes are drilled at regular intervals. The cam chamber 5 is provided with the rotating shaft 3.
A disc cam 13 that is mounted on the shaft and curved into a corrugated plate shape.
is rotatably provided, and a double-headed piston 8 is provided in each cylinder bore 4 through a cam chamber 5.
is inserted so that it can move forward and backward. Furthermore, 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 is transmitted to each piston 8 as a reciprocating motion through the sliding rotation of the roller. It is set up so that you can do it. Conventionally, in the disc cam type compressor as described above, the structure of the roller 14 moored between the disc cam 13 and the double-ended piston 8 is formed into a cylindrical shape as shown in both FIGS. 7 and 8. As shown in FIGS. 9 and 10, a roller 14 having a cylindrical shape with a hollow portion has been previously proposed.

[Problem that the invention attempts to solve]

However, when a cylindrical roller 14 is moored between the disc cam 13 and the double-ended piston 8 as shown in both FIGS. 7 and 8, the roller 14
The problem is that noise is generated at the mooring part of the tether. That is, the disc cam 13
The wavy curved surfaces 13' formed on both the front and rear sides of the piston 8 have slightly different radii of curvature between the inner circumferential side (rotating shaft 3 side) and the outer circumferential side. During this time, the distance between the disk cam 13 and the double-headed piston 8 will change slightly, but the cylindrical roller 14 itself cannot absorb this change in distance, so in order to accommodate this change in distance, The roller 14 is moored with a small gap between the inner peripheral side of the disc cam 13 and the double-ended piston 8. By providing a small gap in the mooring portion of the roller 14 in this way, so-called rattling occurs due to the reciprocating movement of the double-headed piston 8 during operation of the compressor.
The impact causes a problem in that noise is generated.

Furthermore, when a hollow cylindrical roller 14 is moored between the disk cam 13 and the double-ended piston 8 as shown in both FIGS. 9 and 10, the roller 1
By interposing the disc cam 13 and the double-headed piston 8 in a state in which the disc cam 4 is slightly compressed and deformed in the inner diameter direction, the distance created between the disc cam 13 and the double-headed piston 8 through the deformation action of the rollers 14 is This allows the double-headed piston 8 to reciprocate without causing play in the mooring part of the roller 14. However, as mentioned above, the change in the roller 1
4 is formed in a hollow cylindrical shape, so it can be used under high load conditions, such as when so-called liquid compression operation is performed at startup, or when high compression operation is performed when the cooling load in the vehicle interior is large. There is a problem in that it causes problems such as deformation and breakage, that is, it does not provide sufficient durability. Incidentally, it is possible to solve this kind of durability problem by increasing the wall thickness of the hollow part, but by increasing the wall thickness of the hollow part in this way, it is possible to improve the durability of the roller 14. As the elastic force increases, the frictional resistance at the mooring portion increases, resulting in an increased degree of wear and a new problem in that a correspondingly large rotational torque is required.

The present invention is an attempt to improve the above-mentioned problems with hollow cylindrical rollers, and prevents deformation and damage of the hollow cylindrical rollers when the compressor is under high load conditions. The problem that needs to be solved lies in making things possible. That is, in the present invention, the roller is formed by a combination of a hollow cylindrical roller and a cylindrical roller in the mooring part of the roller formed between the disk cam and the double-ended piston, and the compressor is operated under normal load conditions. When the compressor is operated under high load conditions, the rotation of the disc cam is transmitted as reciprocating motion to the double-ended piston through the sliding rotation of the hollow cylindrical roller, and when the compressor is operated under high load conditions, the cylindrical roller The above-mentioned problem is solved by transmitting the rotation of the disk cam as a reciprocating motion to the double-ended piston through the sliding rotation of the piston. The 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 in the shape of a corrugated plate is rotatably installed in the cam chamber, and a roller is freely rotatable between the disc cam and the double-ended piston. In a disc cam type reciprocating compressor moored to The piston is installed in series between the disc cam and the double-ended piston along the radial direction. That is, the hollow cylindrical roller is inserted between the disc cam and the double-headed piston in a slightly compressed and deformed state, and the cylindrical roller is installed with a slight gap between the disc cam and the double-headed piston.

[Operation] When the compressor is in normal operating condition, the hollow cylindrical roller is in sliding contact with the disc cam and the double-ended piston, and a state is obtained in which the rotation of the disc cam is transmitted to the double-ended piston as reciprocating motion. . Since the hollow cylindrical rollers are in sliding contact with the disc cam and the double-headed piston in this way, the gap that occurs between the double-headed piston and the disc cam during the process of the double-headed piston moving from the bottom dead center to the top dead center. Changes in the pressure and compression pressure can be absorbed by the elastic deformation of the hollow cylindrical rollers.

When the compressor is in a high-load operating state, the cylindrical rollers are in direct sliding contact with the disc cam and the double-headed piston, and a state is obtained in which the rotation of the disc cam is transmitted to the double-headed piston as reciprocating motion. By achieving a state in which the cylindrical rollers are in direct sliding contact with the disc cam and the double-headed piston in this manner, further deformation and damage of the hollow cylindrical rollers can be prevented.

〔Example〕

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

1 to 4 are drawings showing the first embodiment, and in each drawing, 1 indicates a housing forming the outer shell of the compressor, and 16 similarly indicates a cylinder block. The cylinder block 16 consists of a front cylinder block 16F and a rear cylinder block 16R, and both cylinder blocks 16F,
16R has a bearing part 2F located at its center,
2R is provided, and a rotating shaft 3 is rotatably supported by both bearing portions 2F and 2R. And the same rotation axis 3
One end passes through the front housing 1F (described later) and is connected to an electromagnetic clutch (not shown), which transmits the driving force of the engine (not shown) to the rotating shaft 3 through connection and disconnection of the electromagnetic clutch. It is set up so that it can be done. Further, a plurality of cylinder bores 4 are bored in both cylinder blocks 16F and 16R in parallel with the rotating shaft 3. That is, they are arranged at regular intervals on the same circumference so as to surround the rotating shaft 3. However, each cylinder bore 4
are 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, and each pair of cylinder bores 4 is provided with a valve plate 6, which will be described later.
A compression chamber 7 exists between F and 6R, into which a double-headed piston 8 is inserted so as to be freely retractable.

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 wall in between.
The front valve plate 6F and the rear valve plate 6R have suction ports corresponding to the suction chambers 9F and 9R, and discharge ports corresponding to the discharge chambers 10F and 10R, respectively. Further, the suction port has suction valves 11F and 1 located on the compression chamber 7 side.
1R is provided so as to be able to open and close freely through the suction stroke of the double-headed piston 8, and a discharge chamber 10 is provided at the discharge port.
Discharge valves 12F and 12R are provided on the F and 10R sides so as to be openable and closable 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 roller 14 is moored between the disc cam 13 and the double-headed piston 8 so that the rotation center (center line) thereof extends in the radial direction of the disc cam 13 so that the rollers 14 can freely rotate. It is provided so that it can transmit reciprocating motion to the double-headed piston 8. Thus, the roller 14 is formed by dividing into three rollers 14a, 14b, and 14c, and both the rollers 14a, 14c disposed at both ends are formed into a cylindrical shape with a hollow portion 14' (hereinafter referred to as a "hollow cylinder"). 14a, 14c), both rollers 1
The roller 14b disposed between 4a and 14c is formed in a cylindrical shape (hereinafter referred to as "cylindrical roller 14b").
Both hollow cylindrical rollers 14a and 14c are formed with a diameter slightly larger than the gap (mooring space) formed between the disc cam 13 and the double-headed piston 8, and are slightly compressively deformed with respect to the mooring space. The vessel is moored in the state of That is, both hollow cylindrical rollers 14a,
14c is the wavy curved surface 13' and the double-ended piston 8.
It is moored with a slight interference between the rear and rear of the
The wavy curved surfaces 13' are provided so that they can freely rotate independently with peripheral speeds corresponding to the radius of curvature of the wavy curved surface 13'. The cylindrical roller 14b is formed to have a slightly smaller diameter than the hollow cylindrical rollers 14a and 14c, and there is a slight gap between the wavy curved surface 13' and the rear surface of the double-headed piston 8. moored. That is, the same cylindrical roller 14b has both hollow cylindrical rollers 1.
4a, 14c are formed corresponding to the compressed deformed state, and when both hollow cylindrical rollers 14a, 14c are compressed and deformed beyond the normal amount of compressive deformation, the wavy curved surface 13' and the rear surface of the double-ended piston 8 are formed. It is provided so that a state in which it comes into contact with is obtained. In the above embodiment, the hollow cylindrical rollers 14a and 14c are arranged on both sides of the cylindrical roller 14b with the cylindrical roller 14b in between. It is also possible to arrange cylindrical rollers on the sides.

FIG. 5 is a drawing showing the second embodiment,
Hollow cylindrical rollers 14a are provided at both ends of the cylindrical roller 14c,
A small diameter stepped portion 15, corresponding to the hollow portion 14' of 14c,
15 is formed, and the hollow portions 14' of the hollow cylindrical rollers 14a, 14c are loosely fitted into the small diameter stepped portions 15, 15.

FIG. 6 is a drawing showing the third embodiment,
In both of the above embodiments, the rollers 14 include a plurality of hollow cylindrical rollers 14a, 14c and a single cylindrical roller 14.
In contrast, in this embodiment, a single hollow cylindrical roller 14a is formed in combination with a single cylindrical roller 14b.

Next, a first embodiment will be described whose operation is shown in FIGS. 1 to 4.

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. And the wavy curved surface 1 of the disk cam 13
3' and the rear and rear surfaces of the double-headed pistons 8, the rotation of the disc cam 13 is transmitted to the double-headed pistons 8 through the sliding rotation of the rollers 14, and each double-headed piston 8 A state of continuous reciprocating movement within the cylinder bore 4 is obtained. When the compressor is operating under normal conditions, the hollow cylindrical rollers 14a and 14b are in sliding contact with the disk cam 13 and the double-ended piston 8 with a slight interference. ,
During the process of the double-headed piston 8 moving from the bottom dead center to the top dead center, the rear surface of the double-headed piston 8 and the wavy curved surface 1
3' and the change in spacing that occurs between the two-headed piston 8.
The compression pressure applied to the hollow cylindrical rollers 14a, 14c
The absorbing action is obtained by the elastic deformation of the material. That is, the effect of preventing the generation of noise can be obtained. Also, when a so-called liquid compression operation is performed at the time of starting the compressor, or when a compression operation is performed under high load conditions such as when a high compression operation is performed, the rear of the double-headed piston 8 A state is obtained in which the cylindrical rollers 14b are in direct sliding contact with the back surface and the wavy curved surface 13' of the disk cam 13. Under such high load conditions, the double-ended piston 8
By achieving a state in which the cylindrical rollers 14b are in direct sliding contact with the disc cam 13, it is possible to prevent abnormal deformation and damage of the hollow cylindrical rollers 14a and 14c beyond their limits.

[Effect of idea]

The present invention is constructed as described above.
As mentioned above, the roller moored between the disk cam and the double-headed piston is divided into a hollow cylindrical roller and a cylindrical roller, and the hollow cylindrical roller is inserted between the disk cam and the double-headed piston while being slightly compressed and deformed. In addition, the cylindrical rollers are formed to have a slightly smaller diameter than the hollow cylindrical rollers, and are inserted with a slight gap between the disc cam and the double-headed piston. During operation, changes in the distance between the disk cam and the double-headed piston and the compression pressure of the refrigerant gas are absorbed through compressive deformation of the hollow cylindrical rollers, and during high loads such as during liquid compression operation or high compression operation. When operating under certain conditions, the cylindrical rollers are brought into direct contact with the disc cam and the double-headed piston, and the rotation of the disc cam is transmitted to the double-headed piston as reciprocating motion. It has now become possible to prevent abnormal compression deformation and damage of the hollow cylindrical rollers. That is,
It has now become possible to improve the durability of the roller.

In the present invention, the rollers are divided and formed by a combination of hollow cylindrical rollers and cylindrical rollers as described above,
During operation under high load conditions, the hollow cylindrical rollers can be made to have a thin wall by making it possible to prevent abnormal compressive deformation and damage of the hollow cylindrical rollers by making them slide into contact with each other. became possible. In other words, it is possible to reduce the reaction force caused by the mooring with a slight interference (compression deformation) between the cylindrical cam and the double-ended piston, thereby reducing the degree of wear on the hollow cylindrical rollers. In addition to being able to reduce the rotational torque during normal operation, it has also become possible to reduce the rotational torque during normal operation.

Furthermore, in the present invention, since the rollers are formed in multiple pieces, it is possible to reduce the difference in circumferential speed between the inner and outer circumferential sides of the disk cam, thereby preventing early wear of the rollers. This made it possible to prevent peeling.

Incidentally, as shown in the second embodiment, by forming small-diameter step portions at both ends of the cylindrical roller and allowing the hollow cylindrical roller to loosely fit into the small-diameter step portions, the assembly is facilitated. In addition to being able to prevent the cylindrical roller from hitting the disc cam, it has also become possible to prevent the generation of noise caused by the impact.

[Brief explanation of drawings]

1 to 4 are drawings showing the first embodiment, in which FIG. 1 is a longitudinal cross-sectional view showing the entire disk cam type compressor, FIG. 2 is an enlarged cross-sectional view of the rollers, and FIG.
The figure is a sectional view taken along the line A-A in FIG. 2, and FIG. 4 is a sectional view showing the operating state of the section taken along the line A-A in FIG.
FIG. 5 is a drawing showing the second embodiment, and is an enlarged sectional view of the roller, and FIG. 6 is a drawing showing the third embodiment, which is also an enlarged sectional view of the roller.
7 and 8 are drawings showing a conventional structure, in which FIG. 7 is a longitudinal cross-sectional view showing the entire disc cam type compressor, and FIG. 8 is an explanatory diagram showing the mooring state of the roller mooring part. . Figures 9 and 10 are drawings showing the same conventional structure, with Figure 9 being a longitudinal sectional view showing the entire disc cam type compressor, and Figure 10 being an explanatory view showing the mooring state of the roller mooring section. be. 1... Housing, 1F... Front housing, 1R... Rear housing, 2F, 2R... Bearing section, 3... Rotating shaft, 4... Cylinder bore,
5...Cam chamber, 6F...Front valve plate, 6R...Rear valve plate, 7...Compression chamber, 8...Double-ended piston, 9F, 9R...Suction chamber, 10F, 10R...Discharge chamber, 11F, 11R
...Suction valve, 12F, 12R...Discharge valve, 13...
... Disc cam, 13'... Wavy curved surface, 14... Roller, 14a, 14c... Hollow cylindrical roller, 14b...
...Cylindrical roller, 14'...Hollow part, 15...Small diameter step part, 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. In the disk cam type reciprocating compressor, the above roller is divided into a combination of a hollow cylindrical roller and a cylindrical roller formed with a slightly smaller diameter than the hollow cylindrical roller, and each roller is formed by a disk cam. A mooring structure for rollers in a disc cam type reciprocating compressor, which is interposed in series between a disc cam and a double-ended piston along the radial direction.