JPS593181A - Opposed swash plate type compressor - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to an opposed swash plate compressor of a new type that does not belong to any of the conventional reciprocating type or rotary type.

[Technical background of 8 Ming and its problems] For example, in a conventional reciprocating electric compressor, a suction valve and a discharge valve are provided in the cylinder chamber, and these valves open and close as the piston reciprocates. This controls the suction and discharge of compressed gas into the cylinder chamber.

However, since each of the above-mentioned valves is composed of a valve plate, it is impossible to accurately follow the movement of the piston, and there is a slight timing delay.

This delay appears as overcompression and overexpansion of the compressed gas, resulting in a decrease in volumetric efficiency. In addition, each valve has the risk of causing metal fatigue and poisoning when used for a long period of time, which is the biggest cause of failure.

On the other hand, compressors such as scroll type compressors and screw type compressors, which are a type of rotary electric compressor, do not require the above-mentioned valves, but on the other hand, the internal structure is complicated and manufacturability is poor.

By the way, for example, Japanese Utility Model Application Publication No. 47-3307, Japanese Utility Model Application Publication No. 47-19806, and Japanese Unexamined Utility Model Application Publication No. 49-'97
Publication No. 313 and the like disclose a structure in which a suction valve is not required in a reciprocating type. Jikoko 53-3
No. 452 discloses a structure that eliminates the need for a suction valve and a discharge valve. However, Japanese Utility Model Publication No. 50-41524 discloses a structure that eliminates the need for a discharge valve in a rotary type.

According to these publications, at least one valve is unnecessary, but the basic structure of either the reciprocating type or the rotary type remains unchanged. Therefore, the compression conditions are affected by modification. In particular, grooves and holes used in place of discharge valves have the same effect as totte clearances, reducing compression efficiency.

In addition, as a completely different compressor structure from the conventional compressor structure, for example, as seen in Japanese Patent Application Laid-Open No. 53-143016,
There is a structure in which a rotating disk and a non-rotating disk pressed by a spring are housed in a casing, and gas to be compressed is sucked between these and compressed. In this case, a new compression method is used, but the mating surfaces of each disc must be tooth-shaped to ensure complete contact, which is extremely troublesome to process and requires a large amount of work since there are many contact parts.・Easy to wear out each other. In addition, a plurality of suction holes and discharge holes for guiding the compressed gas between each disk are provided through each disk and communicated with the recesses of each mating surface. There is a difference in the amount of gas to be compressed, and it is difficult to recognize that effective compression can be achieved. In order to further increase the amount of compression, it is necessary to lengthen the stroke of the non-rotating disk, but this is only possible by increasing the depth of the tooth profile, which further worsens the workability.

[Purpose of the invention]

The present invention aims to provide an opposed swash plate compressor that eliminates the need for movable valves for suction and discharge, has a very simple configuration, has smooth operation, has particularly high compression efficiency, and has improved durability. It is something.

[Summary of the invention]

The present invention provides a piston body housed in a cylinder chamber, comprising a piston receiver having one end surface with a slope and being rotationally driven, and a piston element having one end surface with a slope and elastically pressed and reciprocating. A recess is provided on the slope of the piston receiver to insert the ball so that the rollers make multiple contact with the slope of the piston element, and a groove is provided on the slope in which the ball rolls into contact.
This is designed to reduce the ground clearance volume.

[Embodiments of the invention]

An embodiment of the present invention will be described below based on the drawings. In the figure, 1 is a casing of a compressor, and the inside thereof is partitioned into upper and lower parts by a frame 2. A motor section 3 is provided at the lower part of the frame 2, and a compressor section 4 is provided at the upper part.

The electric motor section 3 includes a shaft 5 pivotally supported by a bearing section 2a provided integrally with the frame 2, a rotor 6 fitted to the shaft 5, and a narrow gap between the outer peripheral surface of the rotor 6. It is composed of a stator 7 arranged therein.

The compressor section 4 is composed of a cylinder 8 disposed on the upper surface of the frame 2, and a piston body P consisting of a piston receiver 9 and a piston element 1o housed in a cylinder chamber 8a inside the cylinder 8. . That is, the piston receiver 9 is integrally provided at the upper end of the shaft 5 and is rotatable. A first slope 11 inclined at a predetermined angle θ1 with respect to the center of rotation is formed on this upper end surface. Fourth
As shown in the figure, the highest part of the first slope 11,
In other words, the diagonally shaded area extending from the top end 11m to the rotational direction side of the piston receiver 9 is selected for the reason described later.
A recess 12h into which a goal 12 as shown in FIGS. 1 to 3 is inserted is provided. The sole 12 protrudes very slightly from the first slope 1 and can freely rotate within the recess 12h. The piston element 10 is located above the piston receiver 9, and a spring 13 is interposed between the piston element 10 and the upper end surface of the cylinder chamber 8a.

Therefore, the lower end surface of the piston element 10 is pressed into elastic contact with the piston receiver 9. A second slope 1"4 inclined at the same angle as the first slope 11 is formed on the lower end surface of the piston element 10. A pair of guide grooves 15, 15 are provided at the upper end of the cylinder 8, and the piston A shaft 17.17 fixed to the shaft 16 of the child 10 can be guided.

That is, the piston element 10 is movable only in the vertical direction without rotating. Further, a suction hole 18 is opened in a part of the peripheral wall of the cylinder 8. This suction hole 18 is connected to the cylinder 8
It communicates with a suction pipe (not shown) via a suction passage 19 provided in the peripheral wall and the frame 2. Further, a discharge hole 20 is located at a position approximately 90° in the counter-rotational direction of the suction hole 18 and the shaft 5.
is opened and communicates with the inside of the casing 1.Furthermore, a groove 21 is provided in the second slope 14 along the circular trajectory drawn by the ball 12 as the ball 12 is driven. The ball 12 is adapted to roll. As shown in FIG. 5, the cross-sectional shape of the groove 2 is preferably a semicircular shape having a radius that is approximately equal to or slightly larger than the radius of the ball 12. Further, the groove 21 may be arranged in a complete annular shape, but as shown in FIGS. 6 and 7, it is arranged in an arc shape with a part of the circle cut off. Furthermore, as shown in FIG. 3, when the piston child 10 reaches the top dead center (the cylinder chamber 8
The groove 21 is formed so that it gradually becomes deeper from both ends so that the depth of the portion where the ball 12 engages is the deepest when the volume of the groove 21 is at its minimum.

Therefore, the inclination angle θ2 of the groove 21 is the same as that of the second slope 14.
The inclination angle θl also increases. Also, piston element 1
Groove 2 where ball 12 engages at the position where 0 reaches top dead center
The depth of the groove is approximately equal to or slightly larger than the height of the groove 12 protruding from the slope 11.

Incidentally, as shown in FIG. 10, an oil supply hole 22 is opened at the bottom of the recess 12a that accommodates the reservoir 12, and this oil supply hole 22 penetrates the piston receiver 9 downward.

The oil supply hole 22 communicates with a distribution groove 23 formed in the bearing portion 2a at least when the piston element 10 is at the bottom dead center as shown in FIG. Further, oil present at the bottom of the casing 1 is supplied to the distribution groove 23 by an oil guide path 24 formed in the shaft 5 when the shaft 5 rotates. That is, this oil guide path 24 is formed in the inclined hole 24 formed inside the shaft 5.
Oil is supplied by the centrifugal force caused by the rotation of the shaft 5 from the spiral groove 24b formed on the outer peripheral surface of the shaft 5 and communicating with the opening of the inclined hole 24IL.

When the piston receiver 9 rotates by energizing the electric motor section 3, the piston element 10 that elastically contacts the piston receiver 9 remains at least partially in contact with the rotation of the piston receiver 9. Move back and forth. Every time the piston receiver 9 rotates once, the first slope 11 changes to the second slope 14.
will be in the same direction.

To explain, when the first slope 11 is inclined in the opposite direction to the second slope 14 as shown in FIG. 2 and FIG. 8 (3), the internal volume between them is maximum. Become.

At this time, the ball 12 comes into contact with the second slope 14 and receives the piston element 1o. The state of (4) is also the same as before, that is, the suction hole 1 is in the position where the rotation of the piston receiver 9 is returned approximately 90 degrees.
8 is opened and compressed gas is sucked in. At this time, the ball 12 does not come into contact with the second slope 14, but the other part of the first slope 11 contacts the second slope 14. During the 90° rotation of the piston receiver 9, the ball 12 comes into contact with the groove 2 of the second slope 14 and receives this while rolling in contact. The piston receiver 9 rotates smoothly with respect to the piston element 10, and the state shown in (A) is passed. Then, the piston element 10 becomes the eighth
As shown in Figure (B), the suction hole 18 is closed by the peripheral wall of the piston receiver 9, and the internal volume between the piston receiver 9 and the piston element 10 becomes smaller. Accordingly, the compressed gas is compressed. Also ball 12
moves to a position away from the second slope 14. Figure 2 (B
) and FIG. 5 (as shown in FIG.
When rotated by 80 degrees, the piston element 10 is in the lowest position, and the first. Since the second slopes 11 and 14 are oriented in the same direction and the internal volume between them is approximately zero, the compressed gas is sufficiently compressed and discharged from the discharge hole 20. Before reaching this state, the sole 12 again moves to the groove 21 of the second slope 14.
The rollers come into contact with each other and smooth the rotation of the piston receiver 9. After passing approximately 180 degrees? - the rule 12 is spaced apart from the second slope 14; When the piston receiver 9 further rotates, the piston element 10 changes to an upward movement. At this time, the largest load of the piston element 10 is applied to the first slope 11. That is, since the load is concentrated when passing through a portion corresponding to the hatched portion of the first slope 11 in FIG. 4, a pole 12 is provided here to enable smooth movement with the piston element 10. When the piston element 10 rises, the internal volume between the slopes 11 and 14 increases, and the compressed gas remaining therein expands. When the suction hole 18 opens, the compressed gas is sucked in again, and the above-described cycle is repeated.

As shown in FIG. 6, when the first slope 11 and the second slope 14 are in direct contact with each other to compress the compressed gas,
Some friction is inevitable. Letting the frictional force be f1 and the friction coefficient μ, then f=R・μ=Ffish θ・μ.

(F: Force due to rotation) The sole 12 damps this frictional force, smoothes the movement, and improves the rotational efficiency of the piston receiver 9.

Furthermore, since sufficient lubricating oil is supplied to the concave portion 12a that receives the pawl 12 during operation, abrasion of the four parts 12h is prevented, and the pawl 12 rotates smoothly, which also reduces the movement of the piston element 10. It becomes smooth.

Further, according to the above configuration, as shown in FIG. 5, the inclination angle θ2 of the groove 11 for the goal receiver is also larger than the inclination angle θl of the second slope 14, so that the piston element 10 is raised upward. At the dead point, the goal 12 falls deepest into the groove 11.

As a result, as shown in FIG. 3, the first slope 11 and the second slope 14 are closer to each other by a distance greater than the amount by which the goal 12 protrudes. The volume efficiency is increased because the volume of the top clearance between the shoulder and both shoulder surfaces 11 and 14 is small. In addition, when the above-mentioned groove 11 is not provided, when the piston child 10 reaches the top dead center, the top clearance volume V is increased by the amount of protrusion of the tail 12.
The larger o is, the lower its volumetric efficiency ηvc is.

P2: Pressure ratio P.

n:f! Redrope index By the way, the depth of the groove 11 is inclined in order to smooth the movement of the piston element 10, but it does not necessarily have to be inclined linearly.

Moreover, since this groove 11 also becomes a part of the above-mentioned top clearance volume, it is better to eliminate the portion other than the portion that contacts the beer 12 at the top dead center as much as possible.

〔Effect of the invention〕

According to the present invention, movable valve bodies for suction and discharge are not required, and the configuration can be simplified, and smooth movement of the piston body can be obtained by the action of the goal, thereby increasing the compression efficiency of the compressed gas. can.

Furthermore, since grooves are formed on the slope where the sol rolls, the top clearance volume can be made much smaller and the compression efficiency can be further increased.

[Brief explanation of drawings]

Fig. 1 is a cross-sectional view of an opposed swash plate compressor showing an embodiment of the present invention, Figs. 2 and 3 are also explanatory diagrams of the operation of the compressor section, and Fig. 4 is a schematic diagram of the piston receiver 7. FIG. 5 is a side sectional view of the piston element, and FIG.
The figure is a perspective view of the piston element, FIG. 7 is a bottom view of the piston element, FIGS. FIG. 10 is an enlarged sectional view showing the operating state of the ball. 8a...Cylinder chamber, 18...Suction hole, 2o...
Discharge hole, 8... Cylinder, P... Piston body, 1 No... First slope, 9... Piston receiver, 14...
2nd slope, 10... piston element, 12... ball, 2... groove. Applicant's agent Patent attorney Takehiko Suzue Figure 2
Figure 3 @ Figure 4

Claims (1)

[Claims] A cylinder having a cylinder chamber and having a suction hole and a discharge hole communicating with the cylinder chamber; and a piston body that discharges the fluid with a piston, and the piston body has a piston receiver which has one end surface as a slope and is rotationally driven, and the piston body is elastically pressed so that the slope formed on the one end surface comes into contact with the slope of the piston support. a piston element which is rotatable and reciprocates in accordance with the rotational position of the piston receiver; a ball which is rotatably provided on the slope of the piston receiver and whose rollers make contact with the slope of the piston element; and a trajectory taken by this goal. It is formed on the slope of the piston element along the slope, and the slope angle of this slope is also set at a large slope angle. - An opposed swash plate compressor characterized by comprising a groove into which the groove passes.