JPS63140881A - Displacement-controlled compressor for car air conditioner - Google Patents

Abstract

PURPOSE:To control the displacement continuously by providing a means moving a cam ring having projections to be coupled with recessed grooves of a casing in the radial direction to the casing. CONSTITUTION:Projections 10, 12 of a cam ring 8 are hermetically slid vertically in recessed grooves 14, 16 of a casing 2. A rotor 26 is rotated by a rotary shaft 28, gas is fed to the first chamber 18 through an intake port 4, enters a compression chamber through an inlet port 22, opens a valve mechanism 25, and is discharged to a discharge port through an outlet port 24 via the second chamber 20. Accordingly, displacement control is facilitated continuously.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to an air conditioner (
The present invention relates to a compressor used in a car air conditioner (hereinafter abbreviated as a "car air conditioner"), and particularly relates to a compressor that controls air flow (1).

[Prior Art and Problems Therewith] In recent years, as comfort in the interior of a vehicle has become more desirable, more and more vehicles are equipped with air conditioners.

A compressor is used in the near conditioner,
In automobiles, the compressor is driven using the output of the engine.

As is well known, in automobiles, the driving rotational force from the output shaft of the engine is transmitted to the drive wheels via clutches, transmissions, etc. and used to drive the automobile, and on the other hand, it is used for the car air conditioner. It is also transmitted to auxiliary equipment such as the compressor, hydraulic pump for power steering, and generator, and is also used to drive the auxiliary equipment.

By the way, a special feature of car air conditioner compressors that does not exist with stationary compressors is that the rotational speed of the output shaft of the engine, which is the drive source for the compressor, fluctuates from a fairly low number (fitting) to a fairly high number. Sometimes it's big. Therefore, if the output of the engine is used directly to drive the compressor, problems will arise. In other words, it is preferable to set the compressor so that it operates sufficiently even when the engine speed is relatively low.
In that case, when the engine speed becomes relatively high, the compressor is driven with more driving force than necessary, resulting in energy loss, which ultimately reduces the acceleration of the vehicle and hinders comfortable driving.

In recent years, there has been a growing demand for automobiles to be particularly fuel efficient and inexpensive, which has led to an increase in the number of automobiles with small engine displacements. Auxiliary equipment such as air conditioner compressors must be driven as efficiently as possible.

Therefore, various methods have been proposed for compressors for car air conditioners to operate under as constant conditions as possible regardless of changes in engine speed, and one of them is a type of compressor that can control the capacity. There is a method of driving with the most suitable capacity for various conditions using .

However, many of the capacity control type compressors conventionally used in car air conditioners are of the reciprocating type, and the capacity can be adjusted in stages by unloading an appropriate number of cylinders. There were many things to change.

However, automobiles are now required to have low noise from the viewpoint of comfort, and reciprocating compressors are unable to fully meet this demand. In addition, the capacity control compressor for a car air conditioner, which has been proposed in the past, has a relatively complicated capacity control structure and a relatively complicated capacity control.

SUMMARY OF THE INVENTION In view of the above-mentioned prior art, an object of the present invention is to provide an improved compressor for a car air conditioner that has a simple and compact structure, produces less vibration and noise, and can easily and continuously control its capacity. shall be.

[Means for Solving the Problems] According to the present invention, in order to achieve the above-mentioned objects, a vane type compressor having a cam ring in a casing has a cam ring installed at substantially opposite positions on the outer surface of the cam ring. A convex line is provided along the axial direction, and a concave groove having a shape corresponding to the convex line is provided on the casing, and the convex line is formed in the concave groove along the radial direction of the cam ring. The cam ring is movably housed in an airtight manner to form a first chamber on the suction side and a second chamber on the discharge side. Provided is a volume control compressor for a car air conditioner, characterized in that a discharge opening on the second chamber side of the compressor is provided with a valve mechanism for preventing backflow from the second chamber into the cam ring. .

[Example] Hereinafter, specific examples of the present invention will be described with reference to the drawings.

FIG. 1(a) is a schematic vertical cross-sectional view showing a main part of an embodiment of a compressor for a car air conditioner according to the present invention, and FIG. 1(b) is a cross-sectional view taken along the line B--B.

In FIG. 1, reference numeral 2 denotes a casing of a sliding vane type compressor, and the casing has a substantially horizontal cylindrical shape, and gas inlets 4 and discharge ports 6 are formed on the side surfaces on both left and right sides.

A cam ring 8 is arranged within the casing 2.

The cam ring has a cylindrical shape having the same directionality as the casing 2.

The upper surface of the cam ring 8 is provided with a protrusion 10 extending in the longitudinal direction of the cam ring. Similarly, a protrusion 12 extending in the longitudinal direction of the cam ring is also provided on the lower surface of the cam ring 8. The left and right sides of these protrusions are parallel planes in the vertical direction, and are airtightly placed in the receiving grooves 14 and 16 formed on the upper and lower sides of the casing 2, respectively, in correspondence with the protrusions 10 and 12. It is housed so that it can be slid.

Thus, the first chamber 18 on the gas suction side is formed as a region surrounded by the left half of the casing 2 and the left half of the cam ring 8, and the gas discharge side is formed as a region surrounded by the right half of the casing 2 and the right half of the cam ring 8. A second side chamber 20 is formed.

Additionally, a gas inlet boat 22 is located on the left side of the cam ring 8.
A gas outlet port 24 is formed on the right side of the cam ring.

The gas outlet boat 24 of the cam ring 8 has a valve mechanism 25.
is attached. The valve mechanism includes an elastic sheet (for example, a rubber seal) 25a for sealing the exit boat 24, a high-strength frame 25b attached to the outer periphery of the elastic sheet, and a frame and sheet that are horizontally rotated. It has a hinge 25C for rotation and a weight 25d attached to the hinge and extending obliquely upward. Therefore, the elastic sheet 25a is always pressed toward the exit boat 24 with a substantially constant force by the action of the way 25d.

26 is a rotor, and 28 is its rotation axis. The rotating shaft has the same directionality as the cam ring 8, and both ends thereof are rotatably held in the casing 2. The rotating shaft 28 is rotated by the driving force transmitted from the engine. A vane 30 is accommodated in a slit formed in the rotor 26, and the vane can slide in the radial direction of the rotating shaft 28.

The L ridge 12 is pushed upward by the other end of a compression coil spring 32 whose one end is supported by the casing 2 . Further, the protruding strip lO is in contact with the rotating cam member 34. The rotating cam member is attached to a rotating ring 36 that is rotatably supported by the casing 2, and moves the protrusion 10 in the vertical direction as the rotating shaft rotates. The rotation angle of the rotation shaft 36 is set by a command from a control means (not shown) for eight-way control of the compressor. In the state shown in FIG. 1, the HP of the cam member 34 with the greatest distance from the rotating shaft 36 is located directly above the rotating shaft 36, and for convenience, the rotation angle of this one stone is assumed to be 0 degrees. In this state, the cam ring 8 is located at the uppermost position, and the lowermost part of the inner surface of the cam ring is in contact with the rotor 26.

FIG. 2 is a partially exploded perspective view of the cam ring 8. End face members 4 for sealing are provided at both axial ends of the cam ring.
2 is fixed. However, the through hole 44 through which the rotor rotating shaft 28 passes is an elongated hole that is elongated in the vertical direction. As shown in FIG. 1(b), the end member 42
The outer surface of the casing 2 is joined to the inner surface of the casing 2 so as to be slidable in the vertical direction. The contact portion between the rotor rotating shaft 28 and the casing 2 is airtightly treated. FIG. 2 shows the relationship between the valve mechanism 25 and the outlet boat 24 more clearly.

Next, the operation of this embodiment will be explained.

FIG. 1(a) shows a case where the rotation angle of the cam member 34 is 0 degrees, and the lowest part of the inner surface of the cam ring is in contact with the rotor 26, and in this state, the maximum discharge amount can be obtained. Note that the rotor 26 is rotated in the direction of the arrow, and the gas is supplied to the suction port 4.
through the first chamber 18 and further into the inlet boat 22
After entering the compression chamber and being compressed at a predetermined compression ratio, the valve mechanism is opened against the biasing force of the valve mechanism 25 and is discharged from the outlet port 24 through the second chamber 20 and through the discharge port 6. .

FIG. 3 is a diagram similar to FIG. 1(a) when the rotation angle of the cam member 34 is 18 degrees. In this state, the cam ring 8 is located at the lowest position, and the rotor rotation shaft 28 is located on the central axis of the cam ring 8. In this state, the discharge amount becomes 0. This is because the gas that has entered the compression chamber from the inlet port 22 is not compressed and returns once inside the cam ring 8 and back into the first chamber 18 from the inlet boat 22. In addition, in this state, the second
The sum of the pressure in the chamber 20 and the biasing force of the valve mechanism 25 is the first chamber 1
8, the elastic sheet 25a of the valve mechanism 25 is pressed toward the outlet port 24, the valve mechanism acts, and backflow is prevented.

Of course, by appropriately setting the rotation angle of the cam member 34, an appropriate state intermediate between the above two states can be realized. In addition, the pressure inside the second chamber 20 and the valve mechanism 2
5 is higher than the pressure inside the compression chamber at the position corresponding to the outlet port 24, the elastic sheet 25a of the valve mechanism 25 is pressed toward the outlet boat 24, and the valve mechanism is activated. Backflow is prevented.

FIG. 4 shows a schematic relationship between the rotation angle of the cam member 34 and the discharge amount. In the case of the above embodiment, it is possible to continuously change the discharge amount from O to the maximum value, as shown by the solid line in FIG.

The cam ring 8 may be modified by appropriately changing the design of the cam member 34.
By appropriately setting the stroke of the vertical movement, the ratio between the maximum discharge amount and the minimum discharge rim can be changed as indicated by the broken line in FIG.

In the above embodiment, the cam member 3 for capacity control
The rotation angle of 4 can be controlled by, for example, a control system (not shown) connected to the rotation shaft 36. Thus, for example, the rotation angle of the cam member 34 can be set to change the capacity according to the detected rotation speed of the engine output shaft (that is, the rotation speed of the rotor rotation shaft 28). Furthermore, for example, it is also possible to detect how much the actual temperature deviates from the set value of the room temperature and set the rotation angle of the cam member 34 in order to change the capacity according to the amount of deviation. Furthermore, the rotation angle of the cam member 34 can be set by detecting the pressure in the second chamber 20 on the discharge side of the compressor and changing the capacity according to the pressure. In this way, the eight arms can be changed based on various conditions, and the capacitance can also be changed in an appropriate manner in order to obtain the best characteristics in consideration of multiple conditions in the control means. .

FIG. 5 is a sectional view of the vicinity of the cam ring to show another embodiment of the valve mechanism 25.

In this embodiment, the vertical relationship between the cam ring 8 and the rotor 26 is opposite to that of the embodiments shown in FIGS.
is located relatively high up. The valve mechanism 25 has an elastic sheet 25a similar to the above embodiment, a frame body 25b similar to the above embodiment, and a hinge 25c similar to the above embodiment. The outlet port 24 is urged against the outlet port 24, and there is an advantage that a special weight like the above embodiment is not required.

FIG. 6 is a perspective view showing another embodiment of the exit boat 24.

In this embodiment, the exit boat 24 has a number of small holes 24.
It consists of a collection of a. According to this, backflow prevention +h
Therefore, there is an advantage that when the valve mechanism 25 is in operation, there is no possibility that the elastic body 25a of the valve mechanism will be drawn into the cam ring 8 and come into contact with the vane 30.

- In the above embodiment, the rotating cam member 34 is employed as a driving means for moving the cam ring in the vertical direction;
In the present invention, driving means using hydraulic pressure or pneumatic pressure or other appropriate means may be used.

[Effects of the Invention] According to the present invention as described above, since it is a rotary compressor, there is little vibration and noise, and since the cam ring is simply moved in one direction, the structure and capacity control are simple.
In addition, the capacity can be continuously controlled, allowing the car air conditioner to operate well while maintaining the comfortable driving performance of the car.In addition, a valve mechanism is attached to the cam ring, which prevents backflow even when the capacity changes frequently. The device can be made more compact without causing any problems, and can fully meet the demand for downsizing of automobiles while maintaining comfort.

[Brief explanation of the drawing]

FIG. 1(a) is a schematic longitudinal sectional view showing the main parts of a car air conditioner compressor according to the present invention, and FIG. 1(b) is a BB sectional view thereof. FIG. 2 is a partially exploded perspective view of the cam ring. FIG. 3 is a schematic vertical cross-sectional view showing the main parts of the compressor for a car air conditioner according to the present invention. FIG. 4 is a diagram showing a schematic relationship between the rotation angle of the cam member and the discharge amount. FIG. 5 is a sectional view of the vicinity of the cam ring. FIG. 6 is a perspective view of the outlet port. 2: Casing, 4: Gas inlet. 6: Gas discharge port, 8: Cam ring, 10.12
: Convex strip, 14, 16: Concave groove, 18: First chamber,
20: Second chamber, 22: Gas inlet port, 24: Gas outlet port, 24a: Small hole. 25: Valve mechanism. 25a two elastic sheets, 25b: frame, 25c: hinge, 25d
: weight, 26: rotor, 28: rotating shaft,
30: Vane, 32: Coil spring, 34:
cam member. 36 two rotation axes. Fig. 2 Fig. 4 Rotation angle

Claims (4)

[Claims] (1) In a vane type compressor having a cam ring inside the casing, protrusions are provided along the axial direction of the cam ring at substantially opposing positions on the outer surface of the cam ring, and the casing has protrusions corresponding to the protrusions. A groove in the shape of the cam ring is provided, and the protruding strip is accommodated in the groove so as to be airtight and movable along the radial direction of the cam ring, and the first chamber on the suction side and the second chamber on the discharge side are accommodated in the groove. A chamber is formed therein, and a means for driving the radial movement of the cam ring with respect to the casing is formed, and a discharge opening on the second chamber side of the cam ring is provided with a means for preventing backflow from the second chamber into the cam ring. A capacity control compressor for car air conditioners, characterized by being equipped with a valve mechanism for (2) The driving means for moving the cam ring moves the cam ring to the first position.
and means for moving the cam ring in a second direction opposite to the first direction against the biasing force in the first direction. Capacity control compressor for car air conditioners. (3) Claim 1, wherein the valve mechanism urges the elastic sheet toward the discharge opening on the second chamber side of the cam ring.
Capacity control compressor for car air conditioners. (4) The capacity control compressor for a car air conditioner according to claim 3, wherein the discharge opening on the second chamber side of the cam ring consists of a large number of small holes.