JPS60259789A - Vane type compressor - Google Patents

Abstract

PURPOSE:To make capacity control performable with certainty without making an energy loss larger, by forming a suction port of a vane type compressor from a circumferential port and a side port, while opening or closing these ports with a slide member in a selective manner. CONSTITUTION:A circumferential suction port 19 is installed in an inner circumferential wall of a cam ring 8 in a vane type compressor at a position where capacity in an actuation chamber comes maximum. Likewise, a side suction port 22 is installed in a front side block at an identical position. A slide controlling member 23 is being installed in the side suction port, and this controlling member is set in slide motion whereby capacity in the compressor is adjustable, but since each suction port is installed in both of the circumferential one and the side block, suction operation takes place without producing any energy loss, no matter what an operation state may be.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a vane compressor used as a refrigerant compressor for, for example, an automobile air conditioner.

(Prior art and its problems) Conventionally, as a vane type compressor whose capacity can be controlled between full operating state and partially operating state by adjusting the suction amount of gas to be compressed, The number is publicly known.

This is a so-called circumferential suction method in which the compressed gas is sucked through a suction port h (circumferential suction port or ferrule suction port) opened on the inner circumferential surface of the cylinder.
A slot along the inner peripheral surface of the cylinder is provided near the suction port of the cylinder, and an arcuate throttle plate that slides within the slot to control the opening area of the suction port. However, with this conventional type, the throttle plate is inserted into the cylinder along its inner circumferential surface, and the end is slidably fitted into the slot, making the configuration complicated and the processing and assembly required. becomes complicated. Furthermore, as described in (b), in the circumferential suction method, the suction efficiency during high-speed operation is good, but the suction efficiency during low-speed operation is reduced.

On the other hand, in the so-called side suction method, in which the compressed gas is sucked in from the suction port (suction port) opened on the sliding surface of the side block with the rotor, which is provided on the end face of the cylinder, the gas is suctioned from the suction port. A bypass port is installed in the cylinder site block to allow the compressed gas to leak into the suction chamber as necessary before it reaches the discharge port.The bypass port is closed during full operation, and the bypass port is closed during partial operation. A device in which a port is opened to allow a portion of the compressed gas once sucked from the suction port to leak from the bypass port 1 to the suction chamber side is also known.

However, this conventional system has a structure in which a part of the compressed scum once compressed leaks to the suction chamber side, which results in wasted work and a large energy loss.In addition, the influence of gas inertia is large, so it is bypassed. The leakage efficiency of scum from the port is therefore poor.

Particularly, control becomes difficult in a partially operating state.

(Object of the Invention) The present invention has been made in view of the above circumstances, and has an object to reliably control the fully operating state and partially operating state by a sliding method with a simple configuration without causing energy loss. purpose.

(Means for Solving the Problems) In order to achieve the above object, the present invention includes a cam ring whose both sides are closed with side blocks, a rotor rotatably disposed within the cam ring, and a rotor of the rotor. A vane type compressor comprising a plurality of vanes slidably fitted in a vane groove, and compressing fluid by varying the volume of a compression chamber defined by the side block, rotor, and vanes. , the circumferential suction port is opened at a position where the volume of the cavity partitioned by the vane on the inner circumferential wall of the cam ring is maximized; The side suction port is opened at a position where the volume of the void chamber divided by , characterized in that a slide control member for controlling the suction angle is provided in a partially operating state in which suction is taken from the circumferential suction port in the first half of the suction stroke, and suction is taken from the side suction port in the second half of the suction stroke. The present invention provides a vane type compressor.

(Example) Hereinafter, an example of the present invention will be described based on the drawings. FIG. 1 shows a longitudinal section of the vane type compressor of the present invention, and in the figure 1
is a housing with a cylindrical case 2 having one end open;
It consists of a front head 4 attached to one end surface of the case 2 with bolts 3 so as to close the opening surface. A discharge port 5 for waste, which is a heat medium, is provided on the top surface of the case 2, and a gas suction port 6 is provided on the top surface of the front head 4.

A pump body 7 is housed inside the housing 1. The pump body 7 includes a cam ring 8 and a cam ring 8.
A front side block 9 and a rear side block 10 are attached to both open ends of the front side block so as to close the opening surfaces,
A rotor 1 is rotatably housed inside the cam ring 8.
1 and a rotating shaft 12 of the rotor 11. The rotating shaft 12 is supported by bearings 14 and 15 provided on both side blocks 9 and 10.

The inner circumferential surface of the cam ring 8 has an elliptical shape as shown in FIG.
, 1.6 are defined.

The rotor 11 is provided with a plurality (for example, four) of vane grooves 17 along the radial direction at equal intervals in the circumferential direction, and the vanes 18° to 18. is fitted so that it can appear and retract freely along the radial direction.

Circumferential suction ports 19 and 19 are opened in the inner circumferential wall of the cam ring 8 at 180 degrees symmetrical positions.

(See Figures 1, 2, and 6) These circumferential suction ports 19, 1.9 should be arranged at positions where the volume of the cavity 16 divided by the vanes tg, 184 is maximum. be. The circumferential suction port 19 has two holes 19+, 1.9+ opening in the inner circumferential wall of the cam ring 8,
One hole 19□ provided inside the circumferential wall of the cam ring 8
The hole 192 opens at the front end surface of the cam ring 8, and the opening connects the front head 4 and the front sight block 9 through a communication hole 20 formed in the front side block 9. It communicates with the suction chamber 21 between. Therefore, the circumferential suction port 19 19 communicates with the suction chamber 21 . The suction angle θl of the circumferential suction port 19 is fixed at the maximum discharge amount.

The front side block 9 is provided with side intake ports 22, 22 at 180 degree symmetrical positions. (Figure 1,
(See Figures 3 to 5) These side suction boats 22
．． 22, like the circumferential suction port 19, is arranged at a position where the volume of the void chamber 16 divided by the vanes 181 to 181 is maximized.

The side suction port 22 has a substantially 1/4 arc shape passing through the front side block 9 in the thickness direction, and the void chamber 16 and the suction chamber 21 communicate with the side suction port 1 via 22. There is.

Side intake port 22 of the front sight block 9
．． 22 are each provided with a slide control member 23 for changing the opening area of these side suction ports 22. (See Figures 1, 3, 4 and 5)
These slide control members 23.23 are plate-shaped and are slidably fitted and held within the side intake port 22.2'2. Said slide control member 23.2
3 are driven in conjunction with each other by a driving means 24. The driving means 24 includes an electric motor 25 as shown in FIGS. 3 and 4.
and a worm 2 fixed to the output shaft 25a of the electric motor 25.
6, and a rotary ring 28 having a gear 27 on a part of its outer circumferential surface that meshes with the worm 26. The rotary ring 28 is rotatably fitted around the outer periphery of the boss portion of the front sight block 9, and is prevented from being removed by retaining rings 29a and 29b. Arms 3 protrude at 180-degree symmetrical positions on the outer circumference of the rotating ring 28.
The protruding end of 0.30 is the slide control member 23.23.
It is connected and fixed approximately at the center of the.

The electric motor 25 is electrically connected to an electronic control device (not shown), and controls air conditioning from an evaporator outlet temperature sensor, a difference sensor between a set temperature and room temperature, a solar radiation sensor, an outside temperature sensor, and a sensor for each part. It is driven based on a drive signal transmitted from an electronic control device in response to information signals necessary for control.

The suction angle of the side suction port 22 during full operation is set to the same angle as the suction angle O5 of the circumferential suction port 19 so as to achieve the maximum discharge amount.

Discharge ports 31° 31 are provided on both side peripheral walls of the cam ring 8.
The discharge chamber 32 inside the case 2 and the cavity chamber 16 communicate with each other through these discharge ports 31, 318-. These discharge ports 32, 32 are equipped with a discharge valve 3.
3 and a discharge valve stop 34 are provided, respectively.

(Function) Next, the function of the vane compressor of the present invention having the above structure will be explained. When the rotating shaft 12 is rotated in relation to the engine of the vehicle and the rotor 11 rotates in the cutting direction in FIG. 6, the vanes 18. ~18. I protrudes radially from the vane groove 17 due to centrifugal force and vane back pressure, and rotates clockwise in the figure while its tip surface slides on the inner peripheral surface of the cam ring 8, and each vane 181~]8. During the suction stroke to expand the volume of the void chamber 16 divided by Then, the gas is compressed in the compression stroke to reduce the volume of the void chamber 16, and in the discharge stroke at the end of the compression stroke, the compressed gas is sequentially passed through the discharge port 31, the discharge chamber 32, and the discharge port 5 to the air conditioner (not shown). heat exchange circuit.

Now, when the slide control member 23 is in the state shown in FIGS. 3 and 7, the suction angle of the side suction port 22 is 01, which is the same as the suction angle of the circumferential suction port 19, and the side suction port 22 is at its starting end 22a. and slide control member 2
3 is open to one end surface 23a. In this state, the first vane 18. passes the starting end 22a of the site suction port 22, the first vane 18. The void chamber 16 divided by the second vane 182 starts to suck in scum, and when the second vane 182 passes one end surface 23a of the slide control member 23, the suction stroke ends and the compression stroke starts. Ru. In the suction stroke when the suction angle is OI, the suction is simultaneously sucked into the cavity 16 from both the circumferential suction port 19 and the side suction port 22.

Also, the suction angle is 0. When the first vane 18° and the second vane 18□ are in symmetrical positions across the major axis Q of the inner peripheral surface of the cam ring 8 at the end of the suction stroke (the start of the compression stroke). The internal volume of the void chamber 16 divided by both vanes 1B and 18□, that is, the suction capacity, becomes maximum, and accordingly, the discharge capacity becomes maximum, resulting in a full operating state and maximum capacity being exhibited.

From this state, the electric motor 25 is rotated in one direction, the rotation ring 28 is rotated counterclockwise in FIG. 3 via the worm 26 and the worm gear 27, and the slide control member 2
3 into the state shown in FIGS. 4 and 8, the suction angle of the side suction port 22 becomes θ2 (approximately twice the suction angle 01 of the circumferential suction port 19), and the side suction port 22 slides with its terminal end 22b. The other end surface 23b of the control member 23
The space between them opens. In this state, it is the first half of the suction stroke.

That is, the first vane 18. From the time when the second vane 182 passes through the starting end 22a of the side suction port 22 until the second vane 182 passes through the other end surface 23b of the slide control member 23, gas is sucked into the gap chamber 16 through the circumferential suction port 19. Also, the second half of the suction stroke, that is, the first vane 18. and the second vane 182 respectively pass through the other end surface of the slide control member 2311- until they pass through the terminal end 23b of the side suction port 22.
Dust is sucked into the cavity 16 from the inside.

Furthermore, at the end of the suction stroke (at the start of the compression stroke) when the suction angle of the side suction port 22 is 02, the first
The internal volume of the cavity 16 divided by the second vane 181 and the second vane 182, that is, the suction capacity, becomes the minimum, and the discharge capacity accordingly becomes the minimum, resulting in a partially operating state at the minimum capacity.

Figure 10 is a curve diagram showing the theoretical discharge amount (double-dashed line) and the actual discharge amount (solid line) when the suction angle is changed from θ to θ2. In the rising section, the suction resistance due to the effect of the throttle increases and the specific volume of the suction gas decreases, resulting in the actual discharge amount being lower than the theoretical discharge amount.On the other hand, in the falling section, the gas inertia increases. As a result, the specific volume of suction sludge increases, so the actual discharge amount increases more than the theoretical discharge amount. Therefore, when setting the suction angle θ1 during full operation and the suction angle 02 during partial operation at the minimum capacity, the curve diagram in FIG. It is desirable to set the

On the other hand, Fig. 9 shows when the suction angle is continuously variable.The suction angle during partial operation at the minimum capacity is determined by 02, but the throttle of the side suction port 22 and the 03 part (when fully operated) Due to the influence of gas inertia trapped in the part located at the difference between the suction angle θ1 and the suction angle 05 during partial operation at intermediate capacity, the discharge amount is
6) increases (or decreases in θ3).

FIG. 11 is a diagram showing the relationship between the suction angle 05 and the discharge amount when the slide control member 23 is at the intermediate position of the side suction port 22, that is, the suction angle θ5. The discharge amount changes continuously while the angle 05 changes from the suction angle 01 at the maximum discharge amount to the suction angle θ2 at the minimum discharge amount.

Although the above embodiment has been described with four vanes, the present invention is not limited to this, and various changes may be made to other configurations without departing from the gist of the present invention. Of course.

(Effects of the Invention) As detailed above, the vane compressor of the present invention includes a cam ring whose both sides are closed with side blocks, a rotor rotatably disposed within the cam link, and a vane of the rotor. A vane type compressor comprising a plurality of vanes slidably fitted in grooves, and compressing fluid by varying the volume of a compression chamber defined by the side block, rotor, and vanes, A circumferential suction port is opened at a position where the volume of the cavity partitioned by the vanes of the inner circumferential wall of the cam ring is maximized, and the -
A side suction port is opened at a position where the volume of the void chamber divided by the vane on the sliding surface side of the side block with the rotor is maximized, and the circumferential suction port and the side suction port are opened on the negative side side block. a full operating state in which suction is taken from both of the side suction ports at the same time, and a partial operating state in which suction is taken from the circumferential suction port on the first half of the suction stroke and from the side suction port on the second half of the suction stroke,
Since it is characterized by the provision of a slide control member that controls the suction angle, it is possible to reliably control the fully operating state and partially operating state with a slide method with a simple configuration without causing energy loss, and it is also possible to control the suction angle in the circumferential direction. Because it has both a side suction system and a side suction system, the suction efficiency does not decrease in both high-speed and low-speed operating conditions, and during partial operation, negative pressure does not occur due to the presence of circumferential suction ports. There is no wasted power loss due to the generation of negative pressure when trying to pull back the vane, and the surface pressure at the tip of the vane does not become excessively high, resulting in effects such as being able to prevent wear and tear.

[Brief explanation of drawings]

The drawings show one embodiment of the present invention, in which Fig. 1 is a longitudinal sectional view of a vane type compressor, Fig. 2 is a perspective view showing a part of the cam ring, and Fig. 3 is a diagram showing the suction angle control mechanism during full operation. Front view, 4th
The figure is a front view of the suction angle control mechanism when it is partially in operation, Figure 5 is a rear view of Figure 3, Figure 15-6 is a vertical sectional view taken along the line Fig. 8 is an explanatory diagram of the action during full operation, and Fig. 8 is an explanatory diagram of the action during partial operation.
Figure 9 is an explanatory diagram of the effect when continuously variable, Figure 10 is a curve diagram showing the relationship between the theoretical discharge amount and actual discharge amount, and Figure 11 is a curve diagram showing the state of change in the discharge amount when continuously variable. be. 8...Cam ring, 9...Front side block, 10...Rear side block, 11...Rotor,
16. Void chamber, 17... Vane groove, 18. ~184・
...Vane, 19...Circumferential suction port, 22...
Side suction port, 23...Slide control member, 24
...Driving means - Applicant: Agent for Decel Equipment Co., Ltd. Patent attorney: Toshihiko Watanabe Agent: Patent attorney Kanji Nagato 1. . 18 Kaisho GO-259789 (6), A3 figure/'/, <'t' 81 Ground 9 figure>P, to figure 811 times θ1 θ2 (candle with lump)

Claims (1)

[Claims] 1. A cam ring whose both sides are closed with side blocks, a rotor rotatably disposed within the cam ring, and a plurality of vanes slidably fitted into vane grooves of the rotor, the side In a vane compressor that compresses fluid by varying the volume of a compression chamber defined by a block, a rotor, and a vane, a position on the inner circumferential wall of the cam ring where the volume of the void chamber divided by the vanes is maximum. A circumferential suction port is opened at the side block, and a side suction port is opened at a position where the volume of the void chamber divided by the vane on the sliding surface side of the - side side block with the rotor is maximized. In the side block on the side, there is a fully operating state in which suction is taken from both the circumferential suction port and the side suction port at the same time, and in the first half of the suction stroke, suction is taken from the circumferential suction port 1-, and in the second half of the suction stroke, suction is taken from the side suction port. 1. A vane type compressor, characterized in that a slide control member is provided for controlling a suction angle in a partially operating state where suction is taken from a suction port.