JPS6330512B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a vane compressor used for compressing a fluid such as a refrigerant.

(Prior art and its problems) There are swash plate type compressors, vane type compressors, etc. as fluid compressors used in air conditioners for vehicles, etc.; Superior volumetric efficiency compared to plate compressors. However, since these compressors are configured to operate in conjunction with the rotation of the engine of a vehicle, etc., the compression capacity of the compressor increases as the rotational speed of the engine (or the rotational speed of the rotor in vane-type compressors) increases. death,
As a result, the cooling capacity of the air conditioner tends to be excessive in the high speed rotation range. On the other hand, to prevent it from getting too cold, turn on the compressor using a thermostat, etc.
OFF switching is now performed, but
In the high-speed rotation range, the cooling capacity becomes excessive as mentioned above, so ON-OFF switching is performed frequently, and as a result, each time the compressor is turned ON, energy that does not contribute to compression work is consumed. The problem is that there is a lot of energy loss.

The present invention was made in view of the above circumstances, and the compressor is controlled by a thermostat etc. in a high rotation range.
It is an object of the present invention to provide a vane type compressor that can minimize the frequency of ON-OFF switching and prevent energy loss that occurs when starting the compressor.

(Means for Solving the Problems) In order to solve the above-mentioned problems, the vane type compressor of the present invention has a vane type compressor in which a chamber comprising a cam ring and first and second side blocks mounted on both sides of the cam ring is provided. , a vane type compressor including a rotor in which a plurality of slits containing vanes are formed, and a fluid suction chamber is formed on the side opposite to the rotor of the first side block, and as the rotor rotates, the direction of rotation of the rotor changes. A groove into which fluid flows from the front slit or the peripheral edge of the rotor is formed between the slits on the side surface of the rotor that slides into contact with the first side block, and the groove is formed between the slits and the suction chamber of the first side block. A suction port is formed in a corresponding portion, and the rotor radially outer end surface, which receives the velocity pressure of the fluid passing through the suction port, gradually moves toward the rotor rotation center side as it goes from the vane side to the suction chamber side. A sliding body having an inclined surface and biased outward in the rotor radial direction by a spring is disposed so as to be slidable in the rotor radial direction, and the sliding body is arranged so as to be slidable in the rotor radial direction, and the sliding body so that the engagement distance between the rotor and the sliding body along the rotor radial direction outside the outer circumferential edge of the groove in the rotor radial direction changes, and when the rotational speed of the rotor is below a predetermined value, the engagement distance is changed. By keeping the engagement distance at a predetermined value, the fluid in the groove does not escape to the suction port, and when the rotational speed of the rotor is greater than or equal to a predetermined value, the engagement distance is reduced to a predetermined value or less. Accordingly, the fluid in the groove is configured to escape to the suction port.

(Function) In the low-to-medium speed range of the engine, the biasing force of the spring maintains a sufficient engagement distance between the rotor and the sliding body outside the rotor's radial outer circumferential edge of the groove. No fluid escapes to the suction port.
On the other hand, in a high-speed rotation range, due to the velocity pressure of the fluid acting on the inclined surface of the sliding body, the sliding body is displaced inward in the radial direction of the rotor against the biasing force of the spring, and the outer circumference of the groove in the radial direction of the rotor Since the engagement distance between the rotor and the sliding body further outwards is reduced and the fluid in the grooves escapes to the suction port, the compression capacity is reduced and the cooling capacity of the air conditioner is suppressed.

(Embodiments) Hereinafter, embodiments of the present invention will be described in detail with reference to FIGS. 1 to 5.

1 and 2, a rotor 4 is rotatably disposed in a chamber consisting of a cam ring 1 and side blocks 2 and 3 mounted on both sides of the cam ring 1. As shown in FIGS. The rotor 4 has a plurality of slits 5 along its radial direction and at equal intervals in the circumferential direction.
are formed, and vanes 6 are fitted into these slits 5 so as to be movable in the radial direction of the rotor 4. The tip surfaces of these vanes 6 always come into sliding contact with the inner circumferential surface of the cam ring 1 due to the centrifugal force generated as the rotor 4 rotates. These vanes 6, cam ring 1, rotor 4, and side blocks 2 and 3 form a pump chamber 7.
is defined. This pump chamber 7 repeatedly expands and contracts as the rotor 4 rotates,
Fluid (refrigerant) is supplied from a fluid suction chamber 8 that communicates with a fluid intake port 9 provided on the outside of the side block 2.
After inhaling, it is compressed and discharged into the discharge pressure chamber 14 through the discharge port 10 provided in the cam ring 1.

Grooves 4a are formed on the side surface of the rotor 4 on the side of the fluid suction chamber 8 between the slits 5, and these grooves 4a have grooves 4a formed in the front direction of the rotor 4 as the rotor 4 rotates. Fluid flows in from the slit 5 and the periphery of the rotor 4.

As shown in FIGS. 2 and 3, the fluid suction chamber 8
A suction port 11 is formed in a portion of the side block (first side block) 2 adjacent to the fluid suction chamber 8, and a suction port 11 is formed within the suction port 11, except for the radial length. Suction port 1
A sliding body 12 having dimensions corresponding to 1 is arranged so as to be slidable in the radial direction of the rotor 4.
An end surface 12a of the sliding body 12 radially outward of the rotor 4 is an inclined surface that gradually slopes toward the rotation center of the rotor 4 as it goes from the vane 6 side to the fluid suction chamber 8 side. . The inner end surface 12 of the sliding body 12 in the radial direction of the rotor 4
b is provided with a recess 12b'. The sliding surface 12c of the sliding body 12 with the rotor 4 is in surface contact with the side surface of the rotor 4, and the groove 4a is
Distance D from the radially inner circumferential edge 4a' of the rotor 4 to the side outer circumferential edge 4b of the rotor 4 (see FIG. 4)
The flat surface has a length along the radial direction of the rotor 4 that is longer than that of the rotor 4.

Furthermore, a notch 12d is formed on the surface of the sliding body 12 that comes into sliding contact with the side wall of the suction port 11, and the notch 12b is formed in the engaging protrusion 11a integrally formed on both side walls of the suction port 11 corresponding to the surface. By abutting and engaging, movement of the sliding body 12 outward in the radial direction of the rotor 4 is restricted.

A spring guide 11b is integrally formed on the inner bottom surface of the suction port 11 in the radial direction of the rotor 4, and a spring 13 is interposed between the spring guide 11b and the recess 12b' of the sliding body. According to
The sliding body 12 is biased outward in the radial direction of the rotor 4, and when the compressor is stopped or rotates at low or medium speed, the sliding body 12 pushes the radially inner peripheral edge of the rotor 4 in the groove 4a. Distance D from 4b' to the outer peripheral edge 4b of the side surface of the rotor 4 (see Figure 4)
It is designed to cover the entire area.

Next, the operation of the vane compressor with the above-described configuration will be explained. The sliding body 12 is urged outward in the radial direction of the rotor 4 by the spring 13, and the outermost position in the radial direction of the rotor 4 is determined by the engaging protrusion 11a, so that the sliding body 12 is not compressed. When the machine is stopped or rotating at low or medium speed, the groove 4 is closed as shown in Figure 4.
The distance "hereinafter simply referred to as (engaging distance)" at which the sliding body 12 and the rotor 4 engage outside the radial outer peripheral edge 4a'' of the rotor 4 in a is D'.

On the other hand, when the rotational speed of the rotor 4 increases in accordance with the rotational speed of the engine, the flow rate of the suction fluid passing through the suction port 11 increases, and the speed pressure increases. Due to the velocity pressure applied to the radially outer end surface 12a, the sliding body 12
are displaced inward in the radial direction of the rotor 4 against the biasing force of the spring 13. In addition, since the velocity pressure is proportional to the square of the flow velocity, in the high-speed rotation range, the spring 13
This is enough to overcome the urging force of Thus,
As shown in FIG. 5, when the outer end 12a of the sliding body 12 in the radial direction of the rotor 4 is located radially inward of the rotor 4 than the outer peripheral edge 4b of the side surface of the rotor 4, the engagement distance d becomes smaller than the engagement distance D' at the time of low/medium speed rotation, and further decreases as the speed pressure increases.

The groove 4a holds pressurized fluid that has flowed from the slit 5 through the space between the rotor 4 and the side block 2 during the compression stroke accompanying the rotation of the rotor 4. Even after passing through the outlet 10, most of the fluid is retained and reaches the sliding body 12 of the suction port 11.

Since the pump chamber 7 where the suction port 11 opens is in a low pressure state and the fluid in the groove 4a is pressurized, the velocity pressure causes the sliding body 12 to
When the engagement distance d decreases by being displaced inward in the radial direction of the rotor 4 against the biasing force of the spring 13, the fluid in the groove 4a easily flows into the pump chamber 7.
It begins to leak. In this case, until part or all of the groove 4a is exposed inside the suction port 11,
It goes without saying that if the sliding body 12 is configured to be displaced, the fluid can flow out more easily. However, even if the groove 4a is not exposed in the suction port 11 and is configured to always leave some engagement distance d, the fluid in the groove 4a is sufficiently pressurized and the pump chamber 7 is kept in a low pressure state. Therefore, the fluid in the groove 4a flows out into the suction port 11 through the gap between the sliding surfaces.

In this manner, by returning the fluid in the groove 4a to the pump chamber 7 during the suction stroke, the volumetric efficiency of the compressor can be reduced and the cooling ability in the high speed rotation region can be controlled.

It goes without saying that if the sliding body 12 is provided for each suction port 11, the compression capacity can be controlled effectively, but it may also be provided for at least one suction port. Further, the shape and arrangement position of the sliding body 12, the spring 13 that biases the sliding body 12, and the engagement protrusion 11a in the suction port 11 can be appropriately set according to various conditions. Further, the groove 4a on the side surface of the rotor 4 is not limited to the illustrated shape, but may be any shape as long as it can be closed by the sliding body 12. Further, in this embodiment, the grooves 4a are provided only on the surface of the rotor 4 on the sliding body 12 side, but providing the grooves 4a on both side surfaces has the effect that lubrication on both side surfaces can be performed well.

(Effects of the Invention) As explained above, the vane type compressor of the present invention has a plurality of slits in which vanes are housed in a chamber consisting of a cam ring and first and second side blocks attached to both sides of the cam ring. In the vane type compressor, in which a fluid suction chamber is formed on the side opposite to the rotor of the first side block, as the rotor rotates, air leaks from the slit in front of the rotor in the rotational direction or from the periphery of the rotor. A groove into which fluid flows is formed between each slit on a side surface of the rotor that slides into contact with the first side block, and a suction port is formed in a portion of the first side block that corresponds to the suction chamber. The radially outer end surface of the rotor, which receives the velocity pressure of the fluid passing through the suction port, is an inclined surface that gradually slopes toward the rotation center of the rotor as it goes from the vane side toward the suction chamber side, and is supported by a spring. A sliding body biased outward in the radial direction of the rotor is disposed so as to be slidable in the radial direction of the rotor, and the outer periphery of the groove in the radial direction of the rotor is adjusted according to the differential pressure between the spring pressure and the velocity pressure of the fluid. The engaging distance between the rotor and the sliding body on the outer side is configured to change along the rotor radial direction, and when the rotational speed of the rotor is below a predetermined value, the engaging distance is maintained at the predetermined value. As a result, the fluid in the groove does not escape to the suction port, and when the rotational speed of the rotor is equal to or higher than a predetermined value, the engagement distance is reduced to a predetermined value or less, so that the fluid in the groove is sucked. It is characterized by being configured so that it escapes to a port.

Therefore, the sliding body is automatically displaced in the direction in which the engagement distance with the rotor decreases as the rotational speed of the rotor increases due to the velocity pressure applied to the inclined surface of the rotor's radially outer end surface, so that the sliding body can be easily - At medium speed rotation, it is possible to obtain the same volumetric efficiency as a conventional vane type compressor, and at high speed rotation, fluid is automatically transferred from the groove to the suction port without the need for a special power source. By venting, the volumetric efficiency of the compressor can be suppressed, and therefore the cooling capacity of the air conditioner is suppressed, and the thermostat is
This has the effect that the frequency of ON-OFF operation switching is reduced, and energy loss that occurs when starting the compressor can be reliably prevented.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional view showing one embodiment of a vane type compressor according to the present invention, FIG. 2 is a sectional view taken along line A-A in FIG. A cross-sectional view, Figure 3 is an enlarged view of the main part of Figure 1, and Figure 4 is a low-level view.
FIG. 5, which is a diagram showing the positional relationship between the rotor and the sliding body during medium-speed rotation, is similar to FIG. 4 during high-speed rotation. DESCRIPTION OF SYMBOLS 1... Cam ring, 2... First side block, 3... Second side block, 4... Rotor, 4a... Groove, 5... Slit, 6... Vane, 8... Fluid suction chamber, 11...Suction port, 1
2...Sliding body, 12a...Rotor radially outer end face, 13...Spring, D', d...Engagement distance.

Claims (1)

[Claims] 1. A rotor in which a plurality of slits containing vanes are formed is disposed in a chamber consisting of a cam ring and first and second side blocks attached to both sides of the cam ring, and a rotor is disposed on the side opposite to the rotor of the first side block. In a vane compressor in which a fluid suction chamber is formed, as the rotor rotates, a slit in the forward direction of the rotor or a groove into which fluid flows from the circumference of the rotor slides into contact with the first side block of the rotor. A suction port is formed between the slits on the side surface and in a portion corresponding to the suction chamber of the first side block, and the suction port has a rotor radius that receives the velocity pressure of the fluid passing through the suction port. The sliding body, whose outer end surface is an inclined surface that gradually slopes toward the rotor rotation center side as it goes from the vane side to the suction chamber side, and which is biased outward in the rotor radial direction by a spring, is moved in the rotor radial direction. The rotor and the sliding body are arranged to be slidable, and the rotor and the sliding body are engaged along the radial direction of the rotor in accordance with the differential pressure between the spring pressure and the velocity pressure of the fluid. When the rotational speed of the rotor is below a predetermined value, the engagement distance is maintained at a predetermined value, so that the fluid in the groove does not escape to the suction port and the rotor 2. A vane type compressor characterized in that when the rotational speed of the vane compressor is equal to or higher than a predetermined value, the engagement distance is reduced to a predetermined value or less, so that the fluid in the groove escapes to the suction port.