JPS597595Y2 - Rotary compressor for vehicles - Google Patents

Description

[Detailed description of the invention] This invention relates to the improvement of a rotary compressor for vehicles, which is equipped with vanes that rotate together with a rotor inside a cylinder and is used as an automobile air conditioner, etc. The present invention provides a highly efficient rotary compressor that solves the problem of vane noise during rotation, has a simple structure, and has stable performance.

A conventional rotary compressor of this type will be explained with reference to FIGS. 6 and 7.

In the figure, a is the cylinder, b is the refrigerant suction port, C is the suction low pressure chamber, d is the compression high pressure chamber, e is the discharge passage, f is the discharge valve, g is the discharge valve holder, h is the cylinder head, and discharge port i Equipped with:

j is the front wall, and k is the rear wall, which forms a bearing for the rotor shaft l and also serves as the side walls of the suction low pressure chamber C and the compression high pressure chamber d.

m is a needle bearing, n is a shaft sealing device, and O is a rotor, which are fastened to the shaft l by press fitting or the like so that they rotate integrally.

The rotor O is provided with a vane slot }p and a vane slot bottom q, into which a vane r is slidably inserted.

Refrigerant gas is sucked into the suction low pressure chamber C from the refrigerant suction port b by the rotation of the rotor O and the vane r, is compressed and pressurized in the state of the compression high pressure chamber d, and is discharged from the discharge port i via the discharge passage e.

In the conventional rotary compressor having the above structure, first, the shaft L and the rotor O are driven via an electromagnetic clutch (not shown).
The rotation begins.

At this time, vane r protruded due to centrifugal force and reached the inner wall of cylinder a, but with this centrifugal force alone, the tip of vane r did not follow the cylinder wall and a collision sound was produced.The sealing performance of the compressed gas was also poor. Compression efficiency also becomes extremely poor.

For this reason, as is well known, the oil pressure from the oil pump (not shown) installed on the opposite side of the input end of the shaft l, or the oil pressure and discharge gas pressure generated on the discharge side, is transferred to the vane slot bottom q.
means for introducing the vane r into the cylinder and pushing the vane r into the cylinder.

That is, as a means for this purpose, pressurizing holes s,
t is provided, hydraulic pressure or gas pressure is introduced from the shaft l to the rotor O through the distribution hole U to the rotor inner circumferential groove V, and pressure is applied from this circumferential groove V to the vane slot bottom q to securely move the vane r. This makes it follow the cylinder wall.

First of all, if hydraulic pressure is used in such a conventional example, it goes without saying that an oil pump is required, and a complicated oil passage must be created, which increases the cost of the oil pump, the cost of processing the oil passage, etc. In addition to the direct cost increase, oil separation functional parts and the like are also required, which is undesirable not only from the cost but also from the viewpoint of performance and quality stability.

Furthermore, when introducing hydraulic pressure and discharge gas pressure to the bottom of the vane slot, it is necessary to create a similarly complicated pressure introduction path, which not only causes an increase in costs, but also requires a means to prevent gas leakage in the pressure introduction path in the middle. This is undesirable not only in terms of cost but also in terms of leakage resistance and stability of performance and quality.

The present invention eliminates the drawbacks of the conventional rotary compressors for vehicles.

Hereinafter, Figures 1 to 1 of the accompanying drawings showing one embodiment of the present invention will be described.
This will be explained with reference to FIG.

In the figure, reference numeral 1 denotes a cylinder, which has spaces each forming a refrigerant suction port 2, a suction low pressure chamber 3, a compression high pressure chamber 4, and a discharge passage 5.

6 is the discharge valve, 7 is the discharge valve holder, 8 is the cylinder head,
A discharge port 9 is featured.

Reference numeral 10 denotes a front wall, and reference numeral 11 denotes a rear wall, which forms a bearing for the rotor shaft portion 12 and also serves as the side walls of the suction low pressure chamber 3 and the compression high pressure chamber 4.

13 is a needle bearing, 14 is a shaft sealing device, and 15 is a rotor, which are made integrally with the shaft portion 12.

Each of the rotors 15 is provided with a vane slot 16 and a vane slot bottom 17, into which a vane 18 is slidably inserted.

The refrigerant gas is sucked into the suction low pressure chamber 3 from the refrigerant suction port 2 by the rotation of the rotor 15 and the vane 18, is compressed and pressurized in the compression high pressure chamber 4, and is discharged from the discharge port 9 via the discharge passage 5.

Reference numeral 19 denotes a gas introduction groove provided on the surface of the vane 18, and the depth of this introduction groove 19 does not exceed the extension of the line of contact between the tip of the vane 18 and the Shinonda 1, and the suction low pressure chamber at the tip of the vane 18 is 3 and the compression high pressure chamber 4 are prevented from directly communicating with each other.

20 is a sealing material, and a recess 21 is provided on the surface.

Reference numeral 22 denotes a slot groove provided in the side wall surface of the vane slot 16 in the rotational direction in the rotor 18, which is similar to the gas introduction groove 1.
9, and the sealing material 20 is inserted.

Here, there is a slight gap between the slot groove 22 and the sealing material 20.

By coming into contact with the gas introduction groove 19, the sealing material 20 partitions the inside of the vane slot 16 into a space 16a on the cylinder inner wall side and a space 16C on the bottom side of the vane slot.

In the above structure, the present invention uses gas introduction on the surface of the vane 18 as a means for directly introducing compressed gas generated as the vane 18 rotates into the vane slot bottom 17 through the gas introduction groove 19 provided on the surface of the vane 18. A sealing material 20 having a backflow prevention function is interposed between the groove 19 and the side wall of the vane slot 16, so that during the compression stroke, that is, when the vane 1
The compressed gas and its mixed oil in the compression chamber 4 are introduced into the vane slot bottom 17 only when the vane 8 is retracted, and the gas pressure in the vane slot bottom 17 is introduced into the suction chamber 3 during the suction stroke, that is, when the vane 18 protrudes. The goal is to hold the material without letting it escape.

Next, its operation will be explained.

Figure 3 shows the vane 18 when it enters the so-called compression stroke.
, the relationship between the rotor 15 and the sealing material 20, and the dashed arrow indicates the flow of gas from the inside of the compression chamber 4 to the vane slot bottom 17.

Moreover, the solid line arrow indicates the moving direction of the vane 18.

In FIG. 3, as the vane 18 moves toward the slot bottom 17 due to the compression process, the seal 20 moves to the left in the figure.

At this time, the high-pressure gas in the compression chamber 4, together with the lubricating oil centrifugally deposited on the cylinder wall, flows into the space 16 as shown in FIG.
a → 16b → recess 21 → space 16C → slot bottom 17
are introduced in this order, pushing the vane 18 in the direction of the cylinder 1.

Next, when the suction stroke begins, the vane 18 is pushed and moved to the right as shown in FIG. 4, and the sealing material 20 also moves to the right in the same way as the vane 18.

At this time, the gas pressure is from slot bottom 17 → space 16 C → recess 2
1, but since the space 16C is closed, it does not reach the suction chamber 3, and the gas in the slot bottom 17 and its mixed oil are retained in the slot bottom 17 as they are.

Here, the inside of the slot bottom 17 is not a completely sealed space, but only a minute gap is sealed with the introduced lubricating oil, so gas and oil leak from the minute gap, and when entering the compression stroke again, the slot bottom It needs to be replenished within 17 days.

However, according to this embodiment, as described above, high pressure gas and lubricating oil are introduced into the vane slot bottom 17 immediately upon entering the compression stroke.

As described above, while the compressor is rotating, the vane slot bottom 17 is replenished with the reduced amount of gas and oil intermittently and during the necessary compression stroke, so the vane 18 is always connected to the cylinder 1.
This will make it follow completely.

In other words, only the insufficient amount of gas and oil is replenished from the compression chamber 4 each time, and there is no unnecessary over-pressure due to high-pressure oil during high-speed rotation, as is the case with conventional oil pumps.
A vane pushing force corresponding to the discharge pressure can be obtained, and a stable operating condition with little input loss and high efficiency can be obtained.

In addition, the structure is simple, and there is no need for oil pumps, oil passages, or oil separation functional parts, making it not only compact but also low in cost.

In addition, in this embodiment, an example of one seal per vane was shown using the slot groove 22 in the rotor and the substantially rectangular seal material 20, but for example, if the slot groove 22 in the rotor is a semicircular stepped groove, the seal material 20 It is also possible to have a cylindrical shape, and a double row seal system such as two seals per vane is also within the scope of the present invention.

As is clear from the above embodiments, the rotary compressor for a vehicle of the present invention has a rotor rotated by a drive shaft disposed in a cylindrical cylinder whose openings on both sides are closed by side walls, and the rotor rotated by a drive shaft. A vane slot opened on the inner wall side of the cylinder is provided, and a vane whose tip abuts against the inner wall surface of the cylinder inside the vane slot partitions the inner space of the cylinder formed by the side wall and the rotor into a suction low pressure chamber and a compression high pressure chamber. is slidably provided, further provided in the rotor is a slot groove extending in a direction intersecting the sliding direction of the vane and opening into the vane slot, and further provided on a surface of the vane facing the slot groove, A surface groove extending in a direction crossing the extending direction of the slot groove is provided, and the slot groove is provided with a surface groove that abuts a surface groove formed on the vane so that the inside of the vane slot including the surface groove is connected to the inner wall side of the cylinder. A sealing member is provided on the bottom side of the vane slot so as to be movable in the sliding direction of the vane, and the sealing member is provided on the bottom side of the slot groove to connect the cylinder inner wall side of the surface groove and the bottom side of the vane slot via this slot groove. The depth of this recess is defined as the depth that separates the cylinder inner wall side of the surface groove that contacts the side wall surface of the slot groove and sandwiches the sealing member when the vane protrudes from the vane slot and the bottom side of the vane slot. Since the sealing member moves in conjunction with the movement of the vane into and out, an appropriate amount of refrigerant gas and lubricating oil are intermittently fed into the bottom of the vane slot and sealed, so the vane is always kept at the optimal pressure. It can be pressed against the inner wall of the cylinder, which eliminates abnormal wear and unnecessary power loss of the vane and cylinder due to excessive pressure of the vane.It also improves the followability of the vane to the cylinder and prevents the generation of abnormal noise or compression. This has various advantages, such as preventing a decrease in efficiency and eliminating the need to complicate the structure by providing a pump means as in the conventional case.

[Brief explanation of the drawing]

Fig. 1 is a sectional view of a rotary compressor for a vehicle according to an embodiment of the present invention, Fig. 2 is a sectional view taken along line A-A in Fig. 1, and Fig. 3 is a slot groove of the same compressor during compression. FIG. 4 is an enlarged sectional view of the main part of the slot groove during suction of the same compressor, FIG. 5 is a sectional view taken along line B-B in FIG. 3, and FIG. 6 is a conventional example. FIG. 7 is a sectional view taken along the line X--X in FIG. 6. 1... Cylinder, 3... Suction low pressure chamber,
4... Compression high pressure chamber, 10.11... Side wall, 15... Rotor, 16... Vane slot, 18... Vane, 19...
Gas introduction groove (surface groove), 20... Seal material, 2
1... Concavity, 22... Slot groove.

Claims (1)

[Scope of utility model registration request] Inside a cylindrical cylinder with openings on both sides closed by side walls,
A rotor rotated by a drive shaft is installed, and this rotor has a
A vane slot opened on the inner wall side of the cylinder is provided,
Furthermore, a vane is slidably provided in the vane slot, the tip of which abuts against the inner wall surface of the cylinder and partitions the inner space of the cylinder formed by the side wall and the rotor into a suction low pressure chamber and a compression high pressure chamber. a slot groove extending in a direction intersecting the sliding direction of the vane and opening into the vane slot; A sealing member is provided in the slot groove to abut on the surface groove formed in the vane and partition the inside of the vane slot including the surface groove into a cylinder inner wall side and a bottom side of the vane slot. The sealing member is provided movably in the sliding direction of the seal member, and further has a recess formed on the bottom side of the slot groove of the seal member, which communicates the cylinder inner wall side of the surface groove with the bottom side of the vane slot via the slot groove,
The depth of this recess is such that when the vane protrudes from the vane slot, it comes into contact with the side wall surface of the slot groove to partition the inner wall side of the cylinder and the bottom side of the vane slot, which sandwich the sealing member. compressor.