JPS61232397A - Vane type compressor - Google Patents

Abstract

PURPOSE:To make it possible to exclude hysteresis characteristic of discharge quantity control, by forming teeth for being driven, on a control member which varies the compression starting position of the suction port of a vane type compressor, and driving this control member directly by a driving means. CONSTITUTION:A control member 19 which varies the compression starting position of the suction port of a vane type compressor, is set at this suction port of the vane type compressor. Teeth 19a for being driven are formed on one side edge of said control member 19, and the output gear of a step motor 20 as a driving means, is engaged with these teeth 19a. As the output of the step motor 20 is transmitted to the control member 19 directly and hysteresis is not generated discharge quantity can be controlled accurately.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a vane compressor used for compressing refrigerant in automobile air conditioners.

(Prior art and its problems) Conventionally, as a so-called variable capacity vane compressor in which the capacity of the vane compressor can be controlled by adjusting the suction amount of gas to be compressed, Utility Model Application Publication No. 55-2000 has been proposed. is publicly known.

Such a conventional vane type compressor has an arc-shaped slot bored through an end plate on the side of the suction port provided in the lower part of the cylinder, and a throttle plate is slidably fitted into the slot. The throttle plate is slid within the slot and the length of the suction port is restricted at its tip, thereby changing the compression start position and variably controlling the discharge volume. Further, one end of a swing lever is connected to the throttle plate via a shaft, the swing lever is pivotally supported by a support shaft fixed to the end plate, and an actuator connected to the other end is connected to the throttle plate. The throttle plate is slidably displaced by rotating the swing lever.

Therefore, since the actuator, which is the driving means, displaces the throttle plate, which is the control member of the suction port, through the swing lever, there are problems such as large hysteresis of the control member and complicated machining and assembly. there were.

(Object of the Invention) The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a vane type compressor that has less hysteresis in discharge volume control and is easy to configure.

(Means for Solving the Problems) In order to achieve the above object, the present invention includes a cam ring whose both end faces are closed with side blocks, a rotor rotatably disposed within the cam ring, and a rotor that is rotatably disposed within the cam ring. a plurality of vanes slidably fitted in the vane grooves of the side block; a control member displaceably attached to the suction port of the one side block; and a drive means for driving the control member; The fluid is compressed by changing the volume of a compression chamber defined by a side block, a rotor, and a vane, and the discharge capacity is variably controlled by changing the compression start position of the suction port using the control member. In the vane compressor, the control member is provided with teeth for being driven, and teeth that mesh with the teeth are provided on the output shaft of the drive means, and the control member is driven by the drive means. The configuration is such that it is directly driven by means.

(Embodiment of the Invention) Hereinafter, an embodiment of the present invention will be described based on the accompanying drawings.

FIG. 1 shows a longitudinal section of a vane type compressor of the present invention, and in the figure, 1 is a housing, which includes a cylindrical case 2 with one end open, and one end of the case 2 with the opening closed. It consists of a front head 3 attached with bolts.

A pump body 4 is housed inside the housing 1 . The pump body 4 includes a cam ring 5, and a front side block 6 and a rear side block 7 mounted on both open ends of the cam ring 5 so as to close the opening surfaces.
The main components are a rotor 8 rotatably housed inside the cam ring 5 and a rotating shaft 9 of the rotor 8, and the rotating shaft 9 is supported by bearings 10 and 11 provided on both side blocks 6. is supported by

The inner peripheral surface of the cam ring 5 has an elliptical shape as shown in FIG.
a, 5b, and compression chambers 12.12 are defined between the inner peripheral surface of the cam ring 5 and the outer peripheral surface of the circular rotor 8 at 180 degrees symmetrical positions.

The rotor 8 is provided with a plurality (for example, five) of vane grooves 13 extending in the radial direction at equal intervals in the circumferential direction, and vanes 14□ to 145 are installed in these vane grooves 13 along the radial direction. It is fitted in such a way that it can appear freely. In this way, the inter-vane volume within the compression chamber 12 is made to vary as the rotor 8 rotates.

As shown in FIGS. 2 to 5, the front side block 6 is provided with circumferential suction ports (peripheral ports) 16, 16 at 180-degree symmetrical positions on the outer circumferential side of one end surface. The circumferential suction port 16 extends from one end surface of the cam ring 5 in the axial direction inside the cam ring circumferential wall, and extends from the vanes 141 to 14 on the inner circumferential surface of the cam ring 5. The compression chamber (between the vanes) is opened in the circumferential direction at a position where the volume of the compression chamber (between the vanes) is maximized during the suction stroke. The suction chamber 17 and the compression chamber 12 are defined between the front head 3 and the front side block 6 through these suction ports 16.16 and communicated with a suction port (not shown) provided in the front head 3. are being communicated.

Further, the front side block 6 is provided with side intake ports 18, 18 at 180 degrees symmetrical positions on the inner peripheral side of one end surface. The side suction port 18 is connected to the front side block 6 by connecting the vanes 14□ to 145 on the sliding surface side of the front side block 6 with the rotor 8.
It is opened at a position where the volume of the compression chamber (between the vanes) divided by (Fig.), the suction chamber 17 and the compression chamber 12 are communicated through these side suction ports 18,18.

Arc-shaped long grooves 6a, 6a along the side intake ports 18, 18 are bored in one end surface of the front side block 6 (Fig. 3). A member 19° 19 is slidably fitted and held (Fig. 5), and as shown in Fig. 1, the presser plate 2
5 prevents movement to the left in the figure. The presser plate 25 is driven by a step motor (driving means) 20.20.
It is also screwed to the front side block 6. As shown in FIG. 6, the control member 19 has toothed portions 19a carved on its outer peripheral surface, and the front side block 6
A protrusion 19b that is slidably fitted into the side suction port 18 is protrudingly provided on the opposite end surface. Further, the step motor 20 has teeth 1 of the control member 19 on the output shaft.
A spur gear is provided having teeth that mesh with 9a.

In this way, the control member 19 is controlled by the step motor 20 with the teeth 19a at a center angle of about 50° from the fully closed position (FIG. 4) to the fully opened position (FIG. 5). It is designed to be continuously rotated over the entire range. In this way, the side suction port 18 has a starting end 18a at its counterclockwise end surface, and a terminal end 18b at its clockwise end surface, that is, the counterclockwise end surface of the control member 19.

The step motor 20 is electrically connected to an electronic control device (not shown), and is necessary for air conditioning control from an evaporator outlet temperature sensor, a difference sensor between a set temperature and room temperature, a solar radiation sensor, or various pressure sensors. It is driven based on a drive signal transmitted from an electronic control device in response to an information signal.

Discharge ports 21° 21 are provided on both side peripheral walls of the cam ring 5.
A discharge chamber 22 in the case 2 and a compression chamber 12 communicate with each other through these discharge ports 21 and 21. These discharge ports 21, 21 are provided with a discharge valve 23 and a discharge valve stop 24, respectively. Note that the discharge chamber 2
2 communicates with a discharge port (not shown) provided in the case 2.

(effect) Next, the operation of the vane compressor having the above configuration will be explained.

The rotary shaft 9 is rotated in relation to the engine of the vehicle, etc., and the rotor 8
When rotates clockwise in FIG. 2, the vanes 141 to 14
s protrudes radially from the vane groove 13 due to centrifugal force and back pressure of the vane, rotates while its tip surface slides on the inner peripheral surface of the cam ring 5, and expands the volume of the compression chamber 12 during the suction stroke (not shown). The refrigerant is sucked into the compression chamber 12 through the intake port, the suction chamber 17 and the suction port 16, the refrigerant is compressed in the compression stroke to reduce the volume of the compression chamber 12, and the compressed refrigerant is compressed in the discharge stroke at the end of the compression stroke. It is supplied to a heat exchange circuit of an air conditioner (not shown) sequentially through the discharge port 21, the discharge valve 23, the discharge chamber 22, and the discharge port (not shown).

As shown in FIG. 2, when the first vane 14□ passes the starting end 16a of the circumferential suction port 16, the first vane 1
41 and the sliding contact portion 5a, the compression chamber 12 is the suction chamber 1.
7 through the circumferential suction port 16, and when the second vane 142 passes the sliding contact portion 5a, the first
The compression chamber 12 partitioned by the second vane 141 and the second vane 14□ continues suction. After that, the second vane 14□
The suction stroke ends when the first vane 141 and the second vane 141 reach the terminal end 16b of the circumferential suction port 16.
The volume of the compression chamber 12 partitioned by the vane 14□ is maximum. Side suction port 1 as shown in Figure 4
8 is fully closed, the first vane 141 and the second vane 141
The compression chamber 12 partitioned off by the vanes 142 starts the compression stroke immediately from the above state. At this time, the compression chamber 12
The refrigerant capacity compressed by this becomes the maximum, and accordingly, the discharge capacity of the compressor becomes the maximum, and the compressor becomes fully operational and its maximum capacity is exhibited.

The control member 19 moves the step motor 2 from the position shown in FIG.
0, the side suction port 18 opens and the starting end 18a and the ending end 18b are separated by a predetermined distance. Then, the first vane 141 and the second vane as described above
After the volume of the compression chamber 12 partitioned by the vanes 142 reaches its maximum, when the rotor 8 further rotates and the volume is reduced, the volume of the compression chamber 12 is increased through the side suction port 18.
The refrigerant inside flows back into the suction chamber 17. second vane 14
When □ passes through the terminal end 18b of the side suction port 18, such backflow of the refrigerant ends and the compression stroke begins. At this time, the amount of refrigerant compressed by the compression chamber 12 decreases by the amount of refrigerant that flows backward. That is, as the terminal end 18b of the side suction port 18 is displaced, the compression stroke start position is displaced clockwise in the figure, thereby reducing the amount of refrigerant in the compression chamber 12. As a result, the discharge capacity of the compressor decreases, resulting in a partially operating state and a decrease in capacity. FIG. 5 shows a state in which the control member 19.19 is displaced to the maximum distance from the starting ends 18a, 18a and the discharge capacity is at its minimum.

The step motor 20 is driven based on various information signals necessary for air conditioning control, and drives and controls the control members 19 and 19 so as to obtain an optimum air conditioning state. In the above embodiment, the step motor 20 is used as the driving means, but the present invention is not limited to this, and an electric motor using a worm gear may be used.

Further, in the above embodiment, each control member 19° 19 is driven and controlled by two drive means separately, but the invention is not limited to this, and a boss located on the outer periphery of the rotation shaft 9 of the front side block 6 can be used. An annular connecting member having teeth carved on the outer peripheral surface thereof is rotatably fitted on the outer circumferential surface of the control member 19, and toothed portions that mesh with the teeth of the connecting member are provided on the inner peripheral surface of each control member 19. The two control members 19.19 are engraved so that they are interlocked via a connecting member so that by driving and controlling one control member 19, the other control member 19 is controlled, and a driving means (step motor) is provided. 20.20 is omitted and only one driving means is used to control the surface control member 19.1.
9 may be controlled.

FIG. 7 shows a second embodiment of the vane type compressor of the present invention, in which the side suction ports 18 and 18' are connected to the vanes 14 on the sliding surface side of the front side block 6 and the rotor 8. The compression chamber (between the vanes) is opened in an arc shape with a center angle of about 50 degrees at a position where the volume of the compression chamber (between the vanes) is the maximum (FIG. 8). Further, an annular groove 6a' along the side intake ports 18' and 1B' is bored in the end surface of the front side block 6 facing the cam ring 5, and an annular control member 26 is formed in this annular groove 1116a'. They are rotatably fitted, and as shown in FIG. 7, one end surface of the cam ring 5 prevents movement in the right direction in the figure. As shown in FIG. 9, the control member 26 has a toothed portion 26a carved on its outer peripheral surface over a center angle of about 60 degrees, and a notch 26b that fully opens the side suction ports 18', 1B' at a predetermined time.

26b are formed at diametrical positions that sandwich the toothed portion 26a substantially symmetrically, and the step motor 20 fixed to one end surface of the front side block 6 by the toothed portion 26a moves the maximum 1st from capacity operating state
The rotation is controlled continuously up to the minimum capacity operating state shown in FIG.

According to the second embodiment described above, since the outer peripheral edge and the inner peripheral edge of the control member 26 do not cross the end face of the compression chamber 12.12, leakage of refrigerant from around the control member 26 is prevented. Ru. Furthermore, since only one step motor 20 is required, controllability is improved and costs are reduced. Further, since the control member 26 is slidably held between the opposing end surfaces of the front side block 6 and the cam ring 5, a member such as the holding plate 25 in the first embodiment is not necessary.

(Effects of the Invention) As detailed above, the vane compressor of the present invention includes a cam ring whose both end faces are closed with side blocks, a rotor rotatably disposed within the cam ring, and a vane of the rotor. The side block includes a plurality of vanes slidably fitted in the grooves, a control member displaceably attached to the suction port of the one side block, and a drive means for driving the control member. , the rotor, and the vane to compress the fluid by changing the volume of the compression chamber defined by the vanes, and to variably control the discharge volume by changing the compression start position of the suction port with the control member. In the vane type compressor, the control member is provided with teeth for being driven, and the output shaft of the drive means is provided with teeth that mesh with the teeth, and the control member is driven by the drive means. Since it is directly driven, hysteresis is reduced, controllability is improved, and machining and assembly are simplified.

[Brief explanation of drawings]

The drawings show embodiments of the present invention, and FIG. 1 is a longitudinal sectional view showing the first embodiment of the vane type compressor of the present invention. Figure 2 is a sectional view taken along the line ■-■ in Figure 1, Figure 3 is an end view of the front side block in Figure 1, and Figure 4 is the mV in Figure 1.
-IV line sectional view, Fig. 5 is the ■-V line sectional view of Fig. 1, 6th w! J is a perspective view of the control member in FIGS. 4 and 5;
The figure is a longitudinal sectional view showing a second embodiment of the vane type compressor of the present invention, FIG. 8 is a sectional view taken along the line ■-■ in FIG. 7, and FIG. 10 and 11 are sectional views taken along the line X--X in FIG. 7. 5...Cam ring, 6,7...Side block, 8
...Rotor, 12...Compression chamber, 13...Vane groove, 14□~14. ...Vane, 16...Circumferential suction port, 18.18'...Side suction port, 19.
26... Control member, 19a, 26a... Teeth, 20
...Step motor (drive means).

Claims (1)

[Claims] 1. a cam ring with both end faces closed by side blocks; a rotor rotatably disposed within the cam ring; a plurality of vanes slidably fitted in vane grooves of the rotor; and the one side. It includes a control member displaceably attached to the suction port of the block, and a driving means for driving the control member, and compresses the fluid by changing the volume of the compression chamber defined by the side block, rotor, and vane. In the vane type compressor, the discharge capacity can be variably controlled by changing the compression start position of the suction port using the control member, and the control member is provided with teeth for being driven. A vane type compressor, characterized in that the output shaft of the drive means is provided with a tooth portion that meshes with the tooth portion, and the control member is directly driven by the drive means.