JPH0755342Y2 - Variable capacity vane compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial field of application) The present invention relates to a plurality of side plates whose volume is changed by rotating a rotor provided with vanes inside a pair of side plates fixed to both open ends of a cylinder. The present invention relates to a vane compressor which sucks gas in a suction chamber into a compression chamber through an intake port and discharges the gas through a discharge port, and more particularly to a variable capacity vane compressor in which a discharge capacity is changed.

(Prior Art) Conventionally, such a compressor is suitably used, for example, as a refrigerant gas compressor for a vehicle interior air conditioner of an automobile. While the air conditioner is operating in a cooling mode that lowers the cabin temperature,
Although a large discharge capacity is required for the compressor, if the room temperature reaches a comfortable temperature and the operating mode of the cooling device shifts to a warming mode that is good enough to maintain that temperature, such a large discharge capacity is not required. Therefore, it is desirable to shift the compressor to a small discharge capacity operation.

Therefore, the applicant of the present invention has proposed the following variable displacement vane compressor in Japanese Patent Laid-Open No. 61-76792. This compressor has a rotor as shown in Figs.
The front side plate 2 and the rear side plate 3 are joined and fixed to the front and rear (left and right in the figure) both ends of the cylinder 1 accommodating 13 with the tightening bolts 11, and the front end face 1a of the cylinder 1 and the rear side face 2a of the front side plate 2 are fixed.
Between the suction chamber and the suction chamber through a through hole formed in the front side plate 2, the amount of the refrigerant gas sucked into the compression chamber during the suction stroke is controlled to control the capacity of the compressor. The rotating plate 32 of the above was interposed.

(Problems to be Solved by the Invention) In this variable displacement vane compressor, since the rotating plate 32 is interposed between the front side plate 2 and the cylinder 1, as shown in FIG. A pressure contact surface S1 between the front end surface 1a of the cylinder 1 and the rear side surface 2a of the front side plate 2 is formed in a substantially annular shape near the outer circumference of the cylinder 1 (see a dotted portion), and a pair of short cylinder bores 1d are formed. The front end surface 1a of the cylinder 1 corresponding to the diameter portion T, that is, the short diameter portion end surface Sf, receives little pressing force because the rotating plate 32 is slidably in contact with the rotating plate 32. Also, cylinder 1
The recesses 1e, 1e for forming the discharge chamber 24 are provided at two locations on the outer periphery of the
Is a notch, so the tightening bolt that holds the recess
11, 11 have a large gap, and therefore the tightening force between the front side plate 2 and the flange portion 1f for forming the discharge chamber located on the front side of the recess 1e in this interval is Y in FIG.
It becomes weaker as shown by (hatched area). The reason why the flange portion 1f is necessary is to prevent the refrigerant gas from leaking to the low pressure side from the high pressure discharge chamber 24 through the gap between the rotary plate 32 and the front end surface of the cylinder 1.

Further, the rear side end surface 1b of the cylinder 1 is entirely the pressure contact surface S2 as shown in FIG. 9 because the rotating plate 32 does not exist between the rear side end surface 1b and the rear side plate 3. (See the dotted area). Therefore, the frictional force between the cylinder 1 and the rear side plate 3 on the rear-side short-diameter portion end surface Sr becomes large.

On the other hand, when the cylinder 1 and both side plates 2 and 3 thermally expand due to the high temperature of the compressed refrigerant gas during the operation of the compressor, the thermally expanded both M2 and M3 of the front side plate 2 and the rear side plate 3 are substantially equal, but Thermal expansion both M1
Is smaller than the thermal expansion amounts M2 and M3 because the inside of the cylinder 1 is hollow, so that the minor axis portion of the cylinder 1 expands in the radial direction due to the frictional resistance of the pressure contact surfaces S1 and S2. Receives the pulling force of. However, as described above, there is no frictional resistance on the end surface Sf of the front side end diameter portion of the cylinder 1, and the front side plate 2 corresponding to the discharge chamber 24 is provided.
The tightening force between the flange portion 1f and the flange portion 1f is weak, while the large frictional force acts on the rear side minor diameter portion end surface Sr as described above, so that the thermal expansion amount M1f of the front side minor diameter portion T of the cylinder 1 is
And the amount of thermal expansion M1r of the rear-side minor diameter portion T increases as the temperature rises, as shown in FIG. As a result,
The clearance C on the rear side at the short diameter portion T between the inner peripheral surface 1c of the cylinder 1 and the outer peripheral surface 13a of the rotor 13 when the compressor is heated.
If you set the dimensions of each member so that r is appropriate,
The predetermined amount of the clear rinse Cf in the short-side portion T on the front side cannot be ensured, and the end portion of the rotor 13 comes into contact with the inner peripheral surface of the front-side cylinder 1 in a high-speed operating state, so that the cylinder 1 and the rotor 13 are in contact with each other. It was worn early and had a problem with the durability of the compressor.

Conversely, if the dimensions of each member are set so that the clearance Cf on the front side becomes appropriate in a heated state, the clearance Cr on the rear side becomes too large, and the clearance Cr from the high pressure side compression chamber to the low pressure side Refrigerant gas easily leaks to the compression chamber,
Clearance on the front side reduces compression efficiency
There was also a problem in increasing Cf.

The object of the present invention is to equalize the amount of thermal expansion on the front side and the rear side in the minor axis portion of the cylinder bore, to optimize the clearance in the minor diameter portion between the rotor and the cylinder, to eliminate galling between the rotor and cylinder, and to improve durability. It is to provide a variable capacity vane compressor that can be improved.

(Means for Solving the Problems) In order to solve the above problems, the present invention encloses a cylinder and both side plates by a front housing forming a suction chamber and a rear housing forming a discharge chamber. Is provided with a through hole that communicates the suction chamber with a compression chamber in the cylinder bore, the cylinder is provided with a discharge port that communicates the compression chamber with the discharge chamber, and the rear side surface of the front side plate and the front end surface of the cylinder are provided. And a rotary plate having an annular shape for controlling the suction amount of the refrigerant gas supplied from the through hole to the compression chamber during the suction stroke so as to be rotatable around the rotary shaft. In the capacity vane compressor, a flange portion is provided on the front side of the recess for forming the discharge chamber formed in the cylinder, and the flange portion is provided on the front side plate. To the rear side of the bets, it adopts a means of connecting the connecting means.

(Operation) In the present invention, the flange portion is provided on the front side of the concave portion for forming the discharge chamber formed in the cylinder, and the flange portion is connected to the rear side surface of the front side plate by the connecting means. In the above, when the compressed high-temperature refrigerant gas causes the cylinder, the front and rear side plates to expand in the radial direction due to heat, a force for forcibly expanding (moving) the flange portion of the cylinder in the radial direction is generated. To work. As a result, the amounts of expansion in the radial direction of the minor diameter portions of the front side and the rear side of the cylinder become the same, and therefore the clearances in the minor diameter portion of the cylinder and the rotor become uniform on the front side and the rear side, and the cylinder on the front side Scoring between the rotor and the rotor is prevented, and durability is improved.

(Embodiment) An embodiment of the present invention will be described below with reference to FIGS.

As shown in FIGS. 3 and 4, a disk-shaped front side plate 2 and a rear side plate 3 which are also made of aluminum are joined to both end surfaces of a cylinder 1 made of aluminum having an elliptic cylindrical hollow portion of the compressor. This forms an elliptic cylindrical space for housing the rotor. A front housing 5 having a suction chamber 4 is provided on the front surface of the front side plate 2, and the suction chamber 4 has a compressor inlet 6
Is communicated with an external circuit via. A rear housing 7 is joined to the rear surface of the front side plate 2 so as to surround the outer peripheries of the rear side plate 3 and the cylinder 1, and a space surrounded by the rear side plate 3 and the rear housing 7 has a mist-like shape in the discharged refrigerant gas. An oil separation chamber 8 for separating oil is formed, and this oil separation chamber 8 is connected to an external circuit via a compressor outlet 9.

The cylinder 1, both side plates 2, 3, both housings
5, 7 are fastened and fixed to each other by eight fastening bolts 11 shown in FIG.

A rotary shaft 10 is rotatably supported in the center of the front side plate 2 and the rear side plate 3 via a plain bearing 12, and has a cylindrical shape formed on the rotary shaft 10 as shown in FIG. Outer peripheral surface 13a of rotor 13
Are housed in close proximity to two locations corresponding to the pair of minor diameter portions T of the cylinder bore 1d, and the rotor is placed in the cylinder bore 1d.
It is divided into a pair of crescent-shaped chambers 14 which are point-symmetric with respect to the central axis of 13. On the circumference of the rotor 13, a plurality of vane grooves 15 (four in this embodiment are shown) are provided over the entire width.
Is formed with a required depth, and the tip of the vane 16 slidably fitted in each vane groove 15 has its tip at the inner peripheral surface of the cylinder 1.
The crescent-shaped chamber 14 is divided into a plurality of compression chambers 17 by being brought into contact with 1c.

A first through hole 20 is formed in the front side plate 2 in the thickness direction of the side plate 2 for guiding the refrigerant gas in the suction chamber 4 to the compression chamber 17 during the suction stroke (increasing the volume). There is. As shown in FIG. 4, the first through holes 20 are located at two points symmetrically with respect to the center of the rotary shaft 10,
Further, it is formed in an arc shape from the short diameter portion T toward the rotation direction of the rotor 13. A suction passage 21 is formed through the cylinder 1 at a position corresponding to the first through hole 20, and a main suction port 22 that communicates the suction passage 21 with the compression chamber 17 is provided through the suction passage 21. Then, the refrigerant gas is sucked from the first through hole 20 into the compression chamber 17 from the suction passage 21 and the main suction port 22 through the second through hole 34 formed in the rotary plate 32 for adjusting the suction amount described later. It is like this.

The compression chamber 17 is communicated with a discharge chamber 24 formed in the cylinder 1 by a discharge port 23 penetrating the cylinder 1. The discharge port 23 is provided with a discharge valve 25 and a retainer 26.
The discharge chamber 24 has a communication passage 27 provided in the rear side plate 3.
Is communicated with the oil separation chamber 8 via.

An oil passage 28 for guiding the oil in the oil separation chamber 8 to the plain bearing 12 is formed in the rear side plate 3, and the rotor side end surface of the rear side plate 3 is also annular oil groove so as to communicate with the vane groove 15. 29 is formed, and the vane groove 15 is also formed on the rotor side end surface of the front side plate 2.
An annular oil groove 30 that communicates with the above is formed. The plain bearing 12, the rotor 13, and the sliding surfaces of the side plates 2 and 3 are lubricated, and a predetermined pressure is applied to the vane groove 15 so that the vane 16 is pressed against the cylinder inner peripheral surface 1c. It has become a force.

A rotating plate 32 for adjusting the suction amount is provided between the front end faces of the cylinder 1 and the rotor 13 and the front side plate 2. The rotary plate 32 is rotatably held around the rotary shaft 10 by a shallow circular groove 33 formed so as to communicate with the annular oil groove 30 on the rear side surface 2a of the front side plate 2. The rear side surface 32a of the front side plate 2 is continuous with the rear side surface 2a of the front side plate 2. Further, in order to allow the rotation of the rotating plate 32, the rear side surface 32a of the rotating plate 32 is in contact with or in close proximity to the front end surfaces of the cylinder 1, the rotor 13 and the vane 16.

The rotating plate 32 has a second through hole penetrating it in the thickness direction.
34 are provided at two locations so as to correspond to the first through holes 20. This second through hole 34 is shown in FIG.
It is possible to change the passage cross-sectional area of the refrigerant gas sucked from the first through hole 20 into the suction passage 21 by adjusting the rotation position of the first through hole 20, and further, the front side surface of the compression chamber 17 is opened so that the auxiliary suction is performed. The port 35 is not provided, and the refrigerant gas is also sucked into the compression chamber 17 during the suction stroke from here.

As shown in FIG. 1, a pin 36 projecting to the side opposite to the rotor 13 is screwed and fixed to the rotating plate 32, and passes through an arc hole 37 formed in the front side plate 2 and then a spool. It is loosely inserted in the long hole 39 formed in 38. The spool 38 is the rotary shaft 10 of the front side plate 2.
It is accommodated in a spool chamber 40 formed in the vicinity of a boss portion that supports the shaft so that it can reciprocate in the same direction as the tangential direction of the rotating plate 32. Then, an appropriate pressure is applied to a high pressure chamber and an intermediate pressure chamber (not shown) formed corresponding to both end faces of the spool 38 in accordance with the cooling load, and when the cooling load is large, the rotating plate 32 is moved to the position shown in FIG. In the above, the rotation is performed in the counterclockwise direction, and when the cooling load is small, the rotation can be automatically performed in the clockwise direction. The automatic control mechanism will be easily understood by referring to, for example, Japanese Patent Laid-Open No. 61-76792.

The main part of the present invention will be described with reference to FIGS. 1 and 3 and 4. The flange part 1f for forming the discharge chamber 24 of the cylinder 1 is described.
A bolt insertion hole 1g is formed in the front side plate 2 corresponding to the insertion hole 1g, and a screw hole 2b is formed in the front side plate 2. The connection bolt 41 as a connecting means screwed from the insertion hole 1g into the screw hole 2b. , The front side plate 2 and the flange portion 1f are fixed by tightening. When the front side plate 2 is heated and expanded in the radial direction, the expansion force causes the flange portion 1f to expand in the same direction into a forced body.

Next, the operation of the vane compressor configured as described above will be described.

When the compressor is started with the rotating plate 32 held in the large capacity position, the rotor 13 and the vanes 16 are rotated by the rotating shaft 10 in the arrow direction of FIG. Then, the refrigerant gas in the suction chamber 4 is discharged into the first through hole 20, the second through hole 34, and the suction passage.
After passing through 21, it is sucked into the compression chamber 17 during the suction stroke and compressed, then discharged from the discharge port 23 to the discharge chamber 24, and further pressure-fed to the oil separation chamber 8 via the communication passage 27.

Since the refrigerant gas compressed in the compression chamber 17 gradually rises in temperature after the compressor is activated, the cylinder 1, the front and rear side plates 2 and 3, the rotor 13, the rotating plate 32, etc. are heated. , And the rotor 13 thermally expands in the axial direction and the radial direction, respectively. At this time, in the embodiment of the present invention, since the front side plate 2 and the flange portion 1f are connected and fixed by the connecting bolt 41, the thermal expansion of the front side plate 2
The flange 1f is forcibly expanded in the radial direction by M2,
As a result, the amounts of thermal expansion M1f and M1r in the radial direction of the front end surface 1a and the rear end surface 1b in the minor diameter portion T of the cylinder 1 become the same as shown in FIGS. 1 and 5, and the inner peripheral surface 1c of the cylinder 1c. The front and rear clearances Cf, Cr in the short-diameter portion T between the rotor 13 and the outer peripheral surface 13a of the rotor 13 are held uniformly and properly. Therefore, the adverse effects such as the deterioration of the sealability due to the galling of the cylinder and the rotor and the increase of the clearance are eliminated, and the durability and reliability are improved.

The present invention can also be embodied as follows.

In the above-described embodiment, the front side plate 2 and the flange portion 1f are fixed by the connecting bolt 41, but instead of this, as shown in FIG. 6 (a), a connecting pin 42 as a connecting means is driven in, As shown in FIG. 6 (b), the front side plate 2 and the flange portion 1f are provided with a concave portion 43 and a convex portion 44, for example, and are arbitrarily modified and embodied without departing from the scope of the claims of the present invention. You can also do it.

Effects of the Invention As described in detail above, the present invention provides a flange portion on the front side of a recess for forming a discharge chamber formed in a cylinder, and the flange portion is provided on a rear side surface of a front side plate.
By connecting by the connecting means, the amount of thermal expansion in the radial direction at the front and rear side minor diameter portions of the cylinder due to the thermal expansion between the front side plate and the rear side plate becomes the same, and the inner peripheral surface of the cylinder and the outer periphery of the rotor are made equal. The clearance between the surface and the minor axis is properly maintained to improve the sealing performance between the cylinder and the rotor, and it is possible to prevent scoring on the inner peripheral surface of the cylinder, improving durability reliability. .

[Brief description of drawings]

1 to 4 show one embodiment of the present invention, FIG. 1 is a front view of the main part showing the rear end face of a cylinder in a variable displacement vane compressor, and FIG. 2 is a cylinder, front and rear. FIG. 3 is a sectional view of a central portion showing the entire variable displacement vane compressor, and FIG. 4 is a sectional view taken along line AA of FIG. 3. FIG. 5 is a graph showing the relationship between temperature and the amount of thermal expansion of the cylinder, FIGS. 6 (a) and 6 (b) are cross-sectional views of only a main part showing another example of the present invention, and FIGS. Shows a conventional example, FIG. 7 is a sectional view showing an assembled state of a cylinder of a variable displacement vane compressor, a side plate and a rotating plate, and FIG. 8 is a front view showing an end surface of a front side of the cylinder. FIG. 9 is a front view showing the rear end face of the cylinder. Cylinder 1, front end face 1a, rear end face 1b, cylinder bore 1d, recess 1e, flange 1f, insertion hole 1g, front (rear) side plate 2 (3), rear side face 2a, screw hole
2b, front side surface 3a, suction chamber 4, front (rear) housing 5 (7), oil separation chamber 8, rotating shaft 10, rotor 13, vane 16, compression chamber 17, first (second) through hole 20 (34) ), Suction passage 21, main suction port 22, discharge port 23, discharge chamber 24, rotary plate 32 for adjusting suction amount, connecting bolt 41 as connecting means, connecting pin 42 as connecting means, and recess as connecting means. 43 and the convex portion 44, the short diameter portion T of the cylinder inner peripheral surface 1c, the expansion amounts M2, M3, the thermal expansion amounts M1f, M1r, and the short diameter portion end faces Sf, Sr.

Claims (2)

[Scope of utility model registration request] 1. A rotor provided with a vane that is rotated by a rotating shaft in a cylinder bore of the cylinder, in which a front side plate and a rear side plate are joined and fixed to both open end faces of a cylinder having an elliptic cylinder shape. The outer peripheral surface of the cylinder bore is housed so as to be in close proximity to each of the two short-diameter portions of the cylinder bore, and the cylinder and both side plates are enclosed by a front housing forming a suction chamber and a rear housing forming a discharge chamber. The side plate is provided with a through hole for communicating the suction chamber with the compression chamber in the cylinder bore, the cylinder is provided with a discharge port for communicating the compression chamber with the discharge chamber, and the rear side surface of the front side plate and the front side of the cylinder are provided. The suction amount of the refrigerant gas supplied from the through hole to the compression chamber during the suction stroke is controlled between the side end surface and the side end surface. In a variable capacity vane compressor in which a rotating plate having an annular shape for rotating is interposed rotatably around the rotating shaft, a flange portion is provided on the front side of the discharge chamber forming recess formed in the cylinder. A variable capacity vane compressor provided with the flange portion connected to the rear side surface of the front side plate by connecting means. 2. The variable capacity vane compressor according to claim 1, wherein the connecting means is a connecting bolt or a connecting pin.