JPS5870085A - Variable capacity type vane compressor - Google Patents

Abstract

PURPOSE:To increase the maximum capacity reducing rate of a variable capacity type vane compressor, by increasing the suction volume of compressed gas by positioning a second suction port forwardly of a succeeding vane of a pair of vanes defining a work chamber having a maximum volume in the direction of rotation of a rotor. CONSTITUTION:A second suction port 29 is formed at a position located forwardly of a succeeding vane 23b of a pair of vanes defining a work chamber 25 having a maximum volume in the direction of rotation of a rotor 22, so that pressure in the work chamber 25 is lowered to the level of suction pressure when a preceding vane 23 has reached the starting edge S of the second suction port 29 and gas is drawn into the work chamber 25 from the port 29 immediately when the vane 23 has passed the starting edge S of the port 29 (at the time, the succeeding vane 23b passes through a first suction port 26). With such an arrangement, it is enabled to reduce the capacity of a variable capacity compressor by a rate corresponding to the volume of the work chamber 25 ranging from the top position P to the starting edge S of the second suction port 29, and this volume provides the maximum reduction volume of the variable capacity compressor.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a variable capacity vane compressor used in vehicle air conditioners and the like.

Generally, in a vehicle air conditioner, when the cabin temperature is high and the cooling load is large, the compressor is operated at 100% capacity, and when the cabin temperature drops and the cooling load is small, the compressor capacity is reduced to 50%, for example. It is suggested that it be done as follows: When this compressor is a vane compressor, the applicant of this application has a structure for reducing its capacity.
Recently, as shown in FIG. 1, during the stroke in which the vane 5 moves from the top position T-P where the rotor 2 is closest to the cylinder 1 to the second suction hole 4 via the first suction hole 3 having a check valve. In the working chamber 6 in the suction state, an injection hole 9 communicating with the working chamber 6 or the discharge chamber 8 in the compression state formed on the way from the second suction hole 4 to the discharge hole 7 is opened, and the injection hole 9 is opened in the working chamber 6 in the suction state. 1. Gas is supplied to the working chamber 6 at an intermediate pressure between the discharge pressure and the suction pressure, or at a discharge pressure. It is proposed that the amount of gas sucked through the second suction holes 3 and 4 is reduced.

However, in the vane compressor described above, the terminal edge e of the second suction hole 4
Since the position of the second suction hole 4 was set so as to correspond to the succeeding vane 5b of the front and rear pair of vanes 5a and 5b forming the working chamber 6 with a maximum volume of , there was a problem that the intake gas amount could be reduced only by the volume from TP to the starting line 8 of the second suction hole 4, and the capacity reduction rate was small.

The present invention has been made in order to eliminate the above-mentioned defects, and its first purpose is to ensure that the terminal edge of the second suction hole is larger than the succeeding vane of the pair of front and rear vanes forming the working chamber with the maximum volume. By providing the second suction hole so as to be located forward in the rotational direction of the rotor, the volume from the top position where the rotor is close to the cylinder to the starting edge of the second suction hole is increased,
An object of the present invention is to provide a vane compressor that can increase the maximum capacity down rate.

A second object of the present invention is to provide an intermediate suction hole between the first suction hole and the second suction hole provided with a check valve in addition to the configuration of the first object, and to set the final edge of the intermediate suction hole to the maximum volume. By making the starting line of the second suction hole correspond to the succeeding vane that forms the working chamber of the vane, the starting line of the second suction hole can be positioned further forward in the rotor rotational direction than the succeeding vane, and the capacity reduction rate can be further increased. An object of the present invention is to provide a vane compressor that can prevent a decrease in capacity during operation.

Hereinafter, a first embodiment that achieves the first object of the present invention will be described as a second embodiment.
To explain FIGS. 4 to 4, front and rear side plates 12 and 13 are fixedly connected to both the front and rear end surfaces of a thick-walled horizontally cylindrical cylinder 11, and a bottomed horizontally cylindrical cylinder is attached to the outer peripheral surface of each member. A llano housing 14 having a shape is fitted and fixed. A front housing 15 is fixedly connected to the front end surfaces of the front side plate 12 and the rear housing 14, and the housing 15 and the front side plate 12 form a suction chamber 16.

In addition, the cylinder 11 and the front side plate 12
The front housing 15 and the front housing 15 are fastened and fixed to each other by a plurality of bolts 17 shown in FIG. )
It is tightened and fixed.

The side plates 12, 13 and the front housing 15 are integrally formed with shaft supporting cylinder portions 12a, 13a and 15a so as to be eccentric from the central axis of the cylinder 11. The shaft support cylinder portion 12a.

A rotary shaft 20 is supported on the shaft 13a via radial needle bearings 1B and 19, and the shaft 20 and the shaft support cylinder 1 are connected to each other.
A shaft sealing machine 1I21 is interposed between 5a. A horizontal cylindrical rotor 22 located inside the cylinder 11 is integrally formed at the intermediate portion of the rotating shaft 20, and both front and rear end surfaces of the rotor 22 are in sliding contact with the end surfaces of the pair of side plays H2, 13, and the outer peripheral surface is the cylinder 11 as shown in FIG.
It is locally in sliding contact with the inner circumferential surface of. Also, rotor 2
A plurality of vane grooves 22a are formed on the outer circumferential surface of the blade 2 over the entire width of the same opening, and a vane 23 is formed in each vane groove 22a.
is removably inserted.

On the other hand, on the outer periphery of the front housing 15, as shown in FIG. 2, a suction port 24 is formed for introducing gas into the suction chamber 16 from the outside.

The suction chamber 16 is connected to the front side plate 12.
From the working chamber in the cylinder 11, that is, the cylinder 11
, the front and rear side plates 12, 13, the rotor 22, and the vane 23 form a first working chamber 25 that sucks gas into a working chamber 25 that changes over time from the suction stroke to the compression stroke.
A suction hole 26 is provided transparently. This first suction hole 26 is located at the top position T-, where the rotor 22 is closest to the cylinder 11.
A mounting member 27 is opened at a position slightly forward in the rotational direction of the rotor 22 from P, and is fixed to the front surface of the front side plate 12 in correspondence with the first suction hole 26, as shown in FIG. A check valve 28 is installed to prevent backflow of gas from the working chamber 25 to the suction chamber 16 during the suction stroke.

Further, the front side plate 12 is provided with a pair of front and rear vanes 23a, 23b forming a working chamber 25 with the maximum volume.
The second suction hole 2 is positioned forward of the following vane 23b in the rotational direction of the rotor 22 (see the dashed line in Figure 3).
9 is formed.

In this embodiment, the starting line S of the second suction hole 29 is made to substantially coincide with the leading edge of the vane 23b, and the ending line e is made to match the leading edge of the vane 23b.
It is located a certain distance e forward from 3b in the rotor rotational direction.

As shown in FIG. 3, a part of the outer periphery of the cylinder 11 is cut out to form a partition 30, and a discharge chamber 31 is formed by the partition 3G, the rear housing 14, and both side plates 12, 13. ing.

The compression stroke working chamber 25 and the discharge chamber 31 communicate with each other through a plurality of discharge holes 32, and a check valve 33 and a retainer 34 are fixed to the partition wall 30 so as to correspond to these discharge holes 32. ing. The rear side plate 13
As shown in FIG. 4, a passage 36 is provided through the rear housing 14 to communicate the discharge chamber 31 with an oil separation chamber 35 formed at the rear of the rear housing 14.

Further, as shown in FIGS. 2 and 3, the rear side plate 13 is provided with a suction state from the oil separation chamber 35 so as to correspond to the working chamber 25 between the top position TP and the first suction hole 26. A reduction hole 37 that can return the gas at the discharge pressure to the working chamber 25 is provided therethrough. The rear side plate 13
A solenoid valve 3B is attached to the rear surface in correspondence with the reduction hole 37, and in a demagnetized state, a spool 40 is pressed against the rear surface of the rear side plate 13 by a spring 39 to close the reduction hole 37, and in an energized state. The spool 40 resists the elasticity of the spring 39 and the rear side plate 13
The reduction hole 37 is opened so as to be spaced apart from the rear surface.

A cap 41 is fixed to the rear end surface of the rear side plate 13 so as to cover the needle bearing 19;
An oil suction hole 42 is provided in the rear side plate 13 so that the inside of the cap 41 and the bottom of the oil separation chamber 35 are communicated with each other. Further, a groove 13b is provided on the front surface of the side plate 13 to communicate the vane grooves 22a with each other, and a passage 13b is provided inside the rotor 13b and the cap 41.
It is connected by c.

As shown in FIG. 4, an oil separation filter 43 is disposed between the inner circumferential surface of the rear housing 14 and the outer circumferential surface of the cap 41, corresponding to the passage 36. Further, the compressed gas in the oil separation chamber 35 is transferred to the outside of the outer periphery of the rear housing 14.Next, the operation of the vane compressor constructed as described above will be explained.

First, when operating at 100% capacity, in this case, the solenoid valve 38 in this embodiment is demagnetized by the control action of the capacity controller (not shown), and the reduction hole 37 is closed by the spool 4o. It is known.

Now, when the rotor 22 is rotated in the direction of the arrow in FIG. 3, the tip of each vane 23 comes into sliding contact with the inner periphery of the cylinder 11 and rotates together with the rotor 22.

In the working chamber 25 in the initial state of suction, the suction chamber 1
Since the pressure will be lower than 6, the first suction hole 26
The check valve 28 opens, and the gas sucked into the suction chamber 16 through the suction port 24 flows into the working chamber 25 through the first suction hole 26. When the preceding vane 23 of the vanes 23 forming this working chamber 25 passes the starting line S of the second suction hole 29, the gas in the suction chamber 16 also flows from this second suction hole 29, and this gas The inflow is performed until the volume of the working chamber 25 is at its maximum, that is, until the subsequent vane 23 forming the working chamber 25 reaches the starting line S of the second suction hole 29.

After the succeeding vane 23 passes the starting line S of the second suction hole 29, the volume of the working chamber 25 gradually decreases.
A portion of the gas sucked into the suction chamber 5 is returned to the suction chamber 16 through the second suction hole 29. This operation causes the subsequent vane 23 to
This is done until it leaves the final edge e of the suction hole 29, but the vane 2
Since the volume change rate within the angle in which 3 rotates from the starting line s to the ending edge e is small, and the backflow of gas is delayed somewhat,
The amount of spillage is small. In this embodiment, if the volume of the working chamber 25 when the succeeding vane 23 leaves the end edge e of the second suction hole 29 is V, and the maximum volume is Vo,
”/vo > 0.9, the subsequent vane 23b and the suction hole 29 are arranged so as to reduce the outflow amount as much as possible.
The distance l from the terminal edge e is set.

Furthermore, the compression of the working chamber 25 starts when the succeeding vane 23 leaves the end edge e of the second suction hole 29, and the working chamber 25 is compressed t.
Sagas is forced into the discharge chamber 31 through the discharge hole 32 . Note that the gas discharged to the discharge chamber 31 passes through the oil separation chamber 35,
It is discharged from the discharge port 44.

Next, when small capacity operation is required due to excess capacity (this is
Due to the control action of the capacity controller, the solenoid valve 38 is energized,
The spool 4o opens the reduction hole 37. Then, the compressed gas in the oil separation chamber 35 passes through the reduction hole 37 and is injected into the working chamber 25 at the beginning of the suction stroke, and the pressure in the working chamber 25 increases almost to the discharge pressure. The flow of this compressed gas into the working chamber 25 is caused by the subsequent vane 2 forming the working chamber 25.
3 passes through the reduction hole 37. The working chamber 25 in this initial suction state corresponds to the first suction hole 26, but since the check valve 28 closes due to the pressure difference, the working chamber 25 corresponds to the first suction hole 26.
Compressed gas does not flow back from 5 to suction chamber 16.

When the rotor 22 further rotates, the compressed gas within the working chamber 25 expands as the volume within the working chamber 25 increases, and its pressure decreases. When this compressed gas expands, the leading vane 23 of the working chamber 25 receives a force in the rotor rotational direction due to the pressure of the gas, so that the rotation of the rotor 22 is promoted.

The leading vane 23 forming the working chamber 25 is connected to the second suction hole 29
Until the compressed gas in the working chamber 25 moves to the starting line S, the compressed gas in the working chamber 25 expands further and its pressure becomes lower than the suction pressure.
The check valve 28 of the first suction hole 26 opens and the gas in the suction chamber 16 flows into the working chamber 25 . When the preceding vane 23 passes through the second suction hole 29, gas begins to flow into the working chamber 25 from the second suction hole 29 as well. After that, when the succeeding vane 23 comes to the starting line sG of the second suction hole 29, the 100%
As in the case of operation at full capacity, the volume of the working chamber 25 becomes large, and a small portion of the inhaled gas is transferred to the suction chamber 16 until the succeeding vane 23 passes the terminal edge e of the second suction hole 29. After returning to the original position, the compression stroke begins, and then the discharge stroke begins. In this discharge stroke, the same amount of compressed gas as during 100% capacity operation is discharged, but the volume of the gas sucked is the same as that of the subsequent vane 23 that flows into the working chamber 25 after passing through the reduction hole 37. Since the volume of the working chamber 25 is reduced by the volume of the working chamber 25 when the compressed gas is expanded and lowered to the suction pressure, the amount of the compressed gas discharged is substantially reduced.

By the way, in this embodiment, the working chamber 2 in the suction state
Gas is sucked into the working chamber 25 from the first suction hole 26 in such a way that the pressure in the working chamber 25 is reduced to the suction pressure before the preceding vane 23 forming the first suction hole 23 moves to the starting line 8 of the second suction hole 29. However, the leading vane 23 is connected to the second suction hole 2.
9, the vane 23 passes through the starting line S so that the pressure in the working chamber 25 drops to the suction pressure (at this time, the following vane 23 has passed through the first suction hole 26). If the gas is sucked into the working chamber 25 from the second suction hole 29 immediately after
The capacity can be reduced by the volume of the working chamber 25 up to the starting line S of the suction hole 29, and this volume becomes the maximum capacity down.

As described above, in the first embodiment of the present invention, the second suction hole 29 is located forward in the rotational direction of the rotor 22 than the succeeding vane 23b that forms the working chamber 25 with the maximum volume. The second
Compared to a conventional vane compressor in which suction holes are located, the suction volume of compressed gas can be increased, and the maximum capacity down rate can be increased.

Next, a fifth embodiment of the second embodiment that achieves the second object of the present invention will be described.
7 to 7 will be explained. Note that the same reference numerals are given to the same or corresponding parts as in the above-mentioned embodiment, and the explanation thereof will be omitted.

In this second embodiment, as shown in FIG. An intermediate suction hole 45 is provided between the hole 26 and the second suction hole 29, and its terminal edge e is aligned with the leading edge e of the succeeding vane 23b. ,
As shown in FIGS. 5 and 7, a first on-off valve 46 and a second on-off valve 47 are installed to correspond to the intermediate suction hole 45 and the second suction hole 29 (as shown in FIGS. 5 and 7). has been done.

As shown in FIG. 5, the first on-off valve 46 includes a spool 49 inserted into the intermediate suction hole 45 so as to be openable and closable in a mounting hole 48 penetrating from the front surface of the front housing 15 so as to communicate with the suction chamber 16; It is composed of a coil spring 50 that biases the spool 49 in the opening direction, a lid 51 that seals the front end of the mounting hole 48, and a valve plate 52 screwed to the rear end of the rod portion of the spool 49. There is.

On the other hand, the rear side plate 13 (this is the solenoid valve 3
A pressure guiding hole 53 that is opened and closed by the spool 40 of B is opened, and this pressure guiding hole 53 is connected to the rear side plate 13.
, the cylinder 11, the front side plate 12, and the front housing 15 to communicate with the pressurizing chamber 54 on the lid 51 side of the mounting hole 48.

As shown in FIG. 7, the other second on-off valve 41 has a mounting hole 55 that penetrates from the front surface of the front housing 15 so as to communicate with the suction chamber 16. A spool 56, a coil spring 51 that biases the spool 56 in the closing direction, and the mounting hole 5.
5, and a valve plate 59 screwed to the rear end of the rod portion of the spool 56.

Furthermore, the pressure guiding hole 53 communicates with the pressurizing chamber 6o on the opposite side from the lid 5B of the mounting hole 55. Note that 61 is a communication hole through which suction pressure is applied to the chamber on the lid 5B side of the attachment hole 55.

Next (2) Two operations of the second embodiment configured as described above will be explained.

First, when operating at 100% capacity (in this case, the solenoid valve 3B is demagnetized, the reduction hole 37 and the pressure guiding hole 53 are closed by the spool 4o, and the spool 49 of the first on-off valve 46 is moved forward by the spring 5o). is moved to the intermediate suction hole 45.
is opened, and the spool 56 of the second on-off valve 47 is opened.
is moved rearward from the spring 57 (the second suction hole 29 is closed). In this state, the rotor 22 is rotated in the direction of the arrow in FIG. 6, and the vane 23 is moved to the top position T.
- When the vane 23 passes through P and passes through the first suction hole 26, gas is sucked into the working chamber 25 from the circulation 26, and when the vane 23 passes through the starting line S of the intermediate suction hole 45, gas is also sucked from the same suction hole 45. , a trailing vane 23 forming a working chamber 25
When is moved to the end edge e of the intermediate suction hole 45, the suction operation is completed, and in this state the volume of the working chamber 25 becomes maximum, and compression starts immediately thereafter. Therefore, in the second embodiment, unlike the first embodiment, during operation at 100% capacity, a part of the gas sucked in is prevented from being returned to the second suction hole 29 or the suction chamber 16, thereby achieving volumetric efficiency. can prevent a decline in

Also, when small capacity operation is required due to excess capacity, the solenoid valve 3 is energized and the spool 40 opens the closed reduction hole 31 and pressure guiding hole 53, which opens the oil separation chamber 35.
Since the compressed gas is supplied to the pressurizing chambers 54, 60 of the first and second on-off valves 46, 47 through the pressure guiding hole 53, the spool 49 is moved rearward in FIG. 5 and opened. At the same time as closing the intermediate suction hole 45, the spool 56 moves forward in FIG. 7 and the second suction hole 29, which had been closed, is opened. This state is similar to the capacity down state in which the electromagnetic valve 38 is opened as described in the first embodiment, so the capacity is reduced as in the first embodiment, but in this second embodiment, the capacity is reduced by 1.
For operation at 00% capacity, close the second suction hole 29 and
9, the second vane 23b, which forms the working chamber 25 with the largest volume,
Even if the starting line S of the suction hole 29 is located forward in the rotational direction of the rotor, it will not affect the 100% capacity operation at all. Therefore, compared to the first embodiment, the starting line S of the second suction hole 29 is The maximum capacity down rate can be increased by the distance from the trailing vane 23b.

Next, a third embodiment that achieves the second object of the present invention will be described with reference to FIG.

In this embodiment, a solenoid valve 62 other than the solenoid valve 38 is attached to the front housing 15 so as to correspond to the second suction hole 29, and a spool 63 of the solenoid valve 62 is attached to the spool 63 to normally close the suction hole 29. However, the other configurations are the same as the second embodiment described in fJiJ.

In this third embodiment, the intermediate suction hole 45 and the second suction hole 29 can be independently controlled by the two solenoid valves 38°62, so that the reduction hole 37 and the second suction hole 29 can be closed and , 100% capacity operation can be performed with the first suction hole 26 and the intermediate suction hole 45 open, and with the reduction hole 37 closed and the first suction hole 2
6. With the intermediate suction hole 45 and the second suction hole 29 open, part of the gas inhaled from the intermediate suction hole 45 and the second suction hole 29 is transferred to the second suction hole after the working chamber 25 reaches its maximum volume. 29 to the suction chamber 16, medium capacity operation can be performed. Furthermore, small capacity operation can be performed with the reduction hole 37 and the second suction hole 29 open and the first suction hole 26 and the intermediate suction hole 45 closed (the intermediate suction hole 45 may be opened). . In addition, in the above-mentioned medium capacity operation (here, the second suction hole 29 functions as a return hole for returning the gas sucked into the working chamber 25 to the suction chamber 16).

It should be noted that the present invention is not limited to the first to third embodiments described above, and can be embodied in the following embodiments.

(1) In each of the embodiments described above, the reduction hole 37 and the oil separation chamber 35 were communicated, but the working chamber 25 during the compression operation and the reduction hole 37 are communicated so that gas at an intermediate pressure between the suction pressure and the discharge pressure is supplied during the suction stroke. The liquid should be injected into the working chamber 25.

(2) Instead of the solenoid valves 38 and 62, the opening is adjusted using a Nubour valve operated by the suction pressure.

(3) To provide the reduction hole 37G with a curling function.

(4) In the embodiment described above, the reduction hole 37 was provided near the top position T-PG where the rotor 22 is close to the cylinder 11 and the cylinder 11.
The suction hole 29 should be arranged so as to open into the working chamber 25 of the suction stroke up to the starting line S.

As described in detail above, the present invention has the effect of increasing the mosquito large capacity down rate and preventing a decline in performance during operation at 100% capacity.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view of a conventional variable displacement vane compressor, FIG. 2 is a longitudinal cross-sectional view showing a first embodiment of the variable displacement vane compressor of the present invention, and FIG. 3 is a cross-sectional view of the same. FIG. 4 is a longitudinal sectional view, FIG. 5 is a longitudinal sectional view showing a second embodiment of the present invention, FIG. 6 is a transverse sectional view of the cylinder position in FIG. 5, and FIG. 7 is a longitudinal sectional view showing the second embodiment of the invention. FIG. 8 is a longitudinal sectional view showing a third embodiment of the present invention. Cylinder 11, front and rear side plates 12
, 13, rotor 22, vane 23, working chamber 25, first suction hole 26, check valve 28, second suction hole 29, reduction hole 37,
Solenoid valve 38.62, intermediate suction hole 45, first and second on-off valves 46.47, top position T-P0 Patent applicant Toyota TFL Automatic Loom Works Co., Ltd. Agent Patent attorney On II Hironobu Figure 1 Figure 1 Figure 2 Figure 3N 4 Figure 4 Figure 5 Figure 6 Figure 7 Figure 8 155

Claims (1)

[Claims] 1. A rotor having vanes is disposed inside the cylinder, and a front side plate and a rear side plate are joined to both front and rear end surfaces of the cylinder, and the cylinder is surrounded by the side plates, the cylinder, the rotor, and the vanes. A first suction hole and a discharge hole each having a check valve are opened in the working chamber so as to be located at the front side and the rear side in the rotational direction of the rotor from the top position where the rotor is closest to the cylinder, and
A second suction hole is opened so as to be located on the front side in the rotor rotational direction relative to the succeeding vane of the pair of front and rear vanes forming a working chamber with a maximum suction volume, and a working chamber for a suction stroke;
Communicates with the working chamber or discharge chamber of the compression stroke through a reduction hole,
A variable capacity vane compressor characterized in that the reduction hole is provided with an on-off valve that opens and closes depending on the load state. 2. The variable displacement vane compressor according to claim 1, wherein a starting edge of the second suction hole substantially coincides with a leading edge of a succeeding vane forming a working chamber with maximum suction volume. 3. The variable displacement compressor according to claim 1, wherein the reducing hole is opened in the working chamber between the top position where the rotor is closest to the cylinder and the first suction hole. 4. A rotor with vanes is installed in the cylinder, and a front side plate and a rear side plate are connected to both front and rear end surfaces of the cylinder. On the other hand, the first suction hole and the discharge hole each having a check valve are opened so as to be located on the front side and the rear side in the rotational direction of the rotor from the top position where the rotor is closest, and the front and rear openings form the working chamber with the maximum suction volume. A second suction hole is opened so as to be located on the front side in the rotor rotational direction than the succeeding vane of the pair of vanes, and an intermediate suction hole is opened so as to be located on the rear side in the rotor rotational direction than the succeeding vane, The intermediate suction hole and the second suction hole are provided with a first on-off valve and a second on-off valve, respectively, and the working chamber for the suction stroke is communicated with the working chamber or the discharge chamber for the compression stroke through a reduction hole. A variable capacity vane compressor characterized in that the reduction hole is provided with an on-off valve that opens and closes depending on the load state. 5. The variable displacement vane compressor according to claim 4, wherein the first on-off valve and the second on-off valve are alternately opened and closed in synchronization with the opening and closing operation of the on-off valve of the reduction hole. 6. The variable capacity vane compressor according to claim 4, wherein the first on-off valve is operated independently, and the second on-off valve is opened and closed in synchronization with the on-off valve of the reduction hole.