JPS5870084A - Variable capacity compressor - Google Patents

Abstract

PURPOSE:To reduce the weight and the size of an electromagnetic clutch and to increase the durability of the same, by decreasing the frequency of ON-OFF switching of the electromagnetic clutch through employment of such an arrangement that the capacity of a compressor can be changed by shifting a particular selector switch in three stages selectively at the time of high-speed operation and low-load operation of the compressor and at the time of starting the compressor. CONSTITUTION:A variable displacement compressor of this invention comprises two by-pass ports Bp, Bp' for communicating a work space and a suction pressure chamber Vs with each other and spools 102, 102' for opening and closing the two by-pass ports Bp, Bp', respectively. Further, a selector valve 105 that can be shifted in three stages is disposed in connecting grooves Pp, Pp' which are extended between a discharge pressure chamber Vd and the two spools 102, 102'. Here, the capacity of the compressor can be varied by shifting the selector valve 105 by a solenoid valve 101 in three stages according to the change of space-cooling load, and opening and closing the two by-pass ports Bp, Bp' in three stages through selective operation of the two spools 102, 102'. With such an arrangement, it is enabled to reduce the frequency of ON-OFF switching of an electromagnetic clutch, to reduce the weight and the size and to increase the durability of the same.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a compressor with an adjustable capacity V4, and more particularly to a compressor with adjustable capacity useful for use in automobile coolers.

The compressor of an automobile cooler is driven by the engine's crank pulley via an electromagnetic clutch, and the compressor rotation speed is used in a wide range of 700 rpm to 6000 rpm, and the cooling load varies from low cooling load A to high cooling load in various environments. used in

However, the capacity of the compressor is mainly determined by the conditions of low rotation and high cooling load, and therefore, the cooling capacity becomes excessive when the cylinder rotation is low and the load is low. When the cooling capacity becomes excessive in this way, the suction pressure of the compressor decreases, the compression ratio increases, and the efficiency of the compressor deteriorates.
This in turn leads to worsening of automobile fuel efficiency. Therefore, the electromagnetic clutch is turned on and off by detecting the cabin temperature, etc.

Although the system is operated in accordance with the cooling load, there is a drawback that the two electromagnets are repeatedly turned on and off during operation, causing acceleration and deceleration, resulting in a poor driving feeling.

Furthermore, when the compressor is started, a step-like drive load is applied to the electromagnetic clutch, but this drive load increases as the capacity of the compressor increases, so it is much larger than the power transmission capacity of the electromagnetic clutch required during steady operation. A compressor with a large capacity is required. In other words, if the capacity of the compressor is the same during startup and steady operation, there is a drawback that an unnecessarily large electromagnetic clutch is used during steady operation.

The present invention was devised in view of the problems of the prior art described above, and reduces the number of on/off operations of the p, The objective is to improve the ring, make the electromagnetic clutch more compact, and improve its durability.

And in order to achieve the above-mentioned object t.

There are two bypass ports that communicate between the compressor's working space and the suction pressure chamber, and a school that opens and closes these two bypass ports. In addition to installing a switchable switching valve.

By providing a solenoid pulp that can create the switching valve in a groove that communicates the switching valve and the discharge pressure chamber, the switching valve can be switched in three stages according to changes in the cooling load. This system is unique in that the two bypasses are opened and closed in three stages by selectively operating the spool, thereby adjusting the capacity IIk of the compressor.

Embodiments of the present invention will be described below with reference to all drawings.

Figures 1 and 2 show -* the variable capacity compressor of the present invention.
This shows an example. In the figure, 1 is a #A driving shaft and rotor, 2 is a vane that penetrates the center of the rotor 1 and is slidable in the radial direction, and 3 is a vane that is slidable in the radial direction as the P-tar l rotates. , bei 7
2 is a liner with a special profile that allows both ends to be in sliding contact at all times; 4 is a drive-side side plate that supports the rotor 1 via the support 8 and is in sliding contact with the sac surface of the base 72;

5 is a rear side plate that restricts the rotor 1 and the vane 2 in the thrust direction. Reference numeral 6 denotes a 70-piece housing which is fixed to the drive side plate 4 via the drive shaft portion of the rotor 1 and a shaft sealing device 9, and 9 is used for fixing an electromagnetic clutch (not shown). The 7Fi rear housing has a discharge valve 7&, is fixed to the rear side grate 5, and forms a high pressure chamber Vd.
is installed on the rear side plate 5! It communicates with the inside of the pulp cover 10 through the through hole 5a. 11 and 12 are fixed to the liner 3 with a discharge valve and a square stopper O. A configuration for variable displacement of the variable displacement compressor according to the present invention is arranged in the drive side side grate 4,
A solenoid pulp 101 that opens and closes in response to a discharge pressure #Pdt-electric signal connecting the high pressure chamber Vd and a specific pressure holding MVb provided in the drive side side plate 4, and a ball 20 provided in the pressure holding chamber vh. A spring 21 that applies a load to this ball 20. A spool 102 that can reciprocate inside the drive-side side plate 4 and opens and closes the bypass port BP disposed on the drive-side side plate 4; 1 distribution discharge pressure chamber V
d in the plunger chamber Vp communicating with the discharge pressure groove Pd'
M movable plunger 105,
rl 05 with load , and a communication hole 110 connecting the pressure holding chamber vh and the end face of the plunger 105,
The other direction of the granger 105 communicates with the suction pressure chamber V8. In addition, the plunger 105 has one hole 105.
A and two holes 105b are connected to each other with a length of 2 m. (See FIG. 4) 4a is a suction valve, and Sp is an inlet for introducing the suction refrigerant into the working space.

The spool guide and school are respectively 1st stage 2
Stage spool guides 104, 104'.

Spools 102 and 102' are provided at two locations each.

Each spool 102, 102 has a pilot groove P.
p and Pp' are derived.

The principle of variable capacity of the variable capacity compressor of the present invention will be explained using FIG. f: communicating bypass bow) Bp.

When both Bp'tj and Bp'tj are closed, the capacity of the compressor is 3rd.
Figure (a) When the middle vane 72 has passed the suction boat 5 pt - shown in 2' and the vane is in the opposite position, the amount of refrigerant gas trapped is normally 2 vanes and the rotor 1. This is the maximum volume formed by the inner edge of liner 3. Next, a case where the capacity is adjusted will be explained. First, in the state shown in FIG. 3 117, one of the bypass bows) Bp and Bp'
The bypass port Bp of the second stage is opened and the suction boat S
p is in communication with the suction pressure chamber v8, and as the compressor capacity at this time decreases as the region of maximum valley volume in IItr decreases with the rotation of the compressor in the n direction, the cold green gas within this maximum volume is It flows from the bypass port Bp of the front stage to the suction pressure chamber v8, and the bypass port of vane 2 or this
What is the weight of the glume area where Bp'i passed and kIji was applied in Figure 3, 1aJ? Approximately 6 to 2 maximum volume to #
The capacity has been reduced to 0%. Next, in the state shown in FIG. 3 1bJ, both the first stage Bp and second stage Bp' of the bypass port are open, and the compressor capacity in this case is 2 even if the rotation further advances in the n direction from FIG. 3 1aJ. The refrigerant flows out from t3p' to the suction pressure chamber Vs, and the bay 72 moves to the second stage bypass port Bp! ! 1
Immediately after the point of impact, the capacity of the next area changes to about 20% of the previous maximum capacity, and the next capacity becomes O. This will be explained using figures. If the solenoid valve 101 is not energized in VC in the figure, the solenoid valve 101 disconnects the discharge pressure groove Fdt.
The pressure in the pressure holding chamber vh is the suction pressure in the suction pressure volume Vll. The jigranger 105 is pushed to the left in the figure by the load of the spring 106, and the discharge groove Pd does not communicate with any hole in the plunger 105 and the spool 102 , 102' becomes suction pressure, so the spools 102, 102'
'Both are in a neutral state, but the bypass board) Bp, B
Due to the force caused by the refrigerant flowing out from p', both spools 102 and 102' move to the left in the figure, and both the first and second stage bypass bows (Bp, Bp') are opened, as described above (20
capacity. When the compressor is started, it is always in this state, and therefore the driving load is significantly smaller than that without variable valleys, and the electromagnetic clutch can be made into a l'' type. Conversely, when the solenoid valve 101 is constantly energized, the discharge groove Pd goes astray and the ball 20 in the pressure holding chamber vh overcomes the load of the spring 21 and the ball 2
0t - The discharge pressure is 0 pressure on the end face of the plunger 105, and the plunger 105 is pushed downward in the same figure.
6, the discharge @Pd' communicates with both pilots #I Pp and Pp' through two holes 105bi in the granger 105, and the spools 102,
Discharge pressure is added to 102' and the cisboule 102, 102'/
fi the first and second stage bypass bows) Bp, βp'
When the compressor is closed, the compressor valley t becomes 100%, and a light cooling operation is performed when the cooling load is large.

Next, when the solenoid valve 101 is intermittently energized, the solenoid valve 101 immediately and continuously communicates the discharge tsPd with the pressure holding chamber vh, and the refrigerant gas in the pressure holding chamber vh is By flowing to the outer circumference of the plunger 105 and finally to the suction chamber V8, the pressure in the pressure holding chamber vh becomes an intermediate pressure between the discharge pressure and the suction pressure. In other words, the discharge #Pd' is connected to the pilot groove Pp through one length 105a in the granger 105.
′ and move to a position delayed by a. For this reason, spool 10
Discharge pressure is applied only to 2', and the first stage bypass port 1
3p is opened, the second stage bypass port Bp' (I-Tsugu Arashi is to be used, and as mentioned above, 60 pieces of congretsa are used)
ft can be realized.

Next, FIG. 5 shows the operation of the entire Tomouri-2 system incorporating the variable capacity compressor according to the invention.

This will be explained using Figure 6. In FIG. 5, 100 is a variable capacity compressor according to the present invention.

200 is a condenser, 300 is a liquid receiver, 400 is an expansion valve, 5
0 (l# generator). 600 is a solenoid 101t-controlled of a non-inventive compressor (I141-). It has a #4 configuration that sends electrical signals to the solenoid pulp.

First, when starting the cooler, the solenoid pulp 101 is set to O.
In the FF state, the compressor capacity becomes 20% as described above, and the compressor/presser is activated by turning on the electromagnetic clutch (not shown). The beginning! Since the temperature t of the cooling air immediately after I/I is high, when the control circuit receives a signal from the thermometer and turns on the solenoid pulp 101i, the compressor 100 examiner will receive a reading of 20% - 460% - 4100%. The Heto F conversion system can produce sufficient cooling effects. Operation continued with a compressor capacity of 100 kg.
Eventually, the temperature of the cooling air reaches the preset temperature t1.
When the pressure drops below 100, the control path 600 sends an intermittent signal to the solenoid pulp 101 to increase the compressor capacity to 100.
%→60%. When the cooling load at this time is 1 less than the cooling capacity obtained by operating the compressor at 60% capacity, the temperature i of the cooling air becomes even lower pt! When this happens, the solenoid pulp 10IU turns off and the compressor capacity becomes 20%. And when the cooling temperature becomes 22 or higher again.

Solenoid pulp 101 is in an intermittent state and operates at 60% compressor capacity. ' If the cooling load increases and the cooling capacity obtained with 60% of the compressor capacity is insufficient, the cooling air will rise once or more.
When lVC is reached, the control circuit is turned on and the compressor capacity becomes 100% again. or.

Cold tj! If the temperature of the cooling air is very small compared to the negative air or cooling air, the temperature of the cooling air will be low even if the compressor capacity is 120%, and the temperature will become below t3, the electromagnetic clutch will be turned off and the compressor will stop rotating (the compressor capacity will be 120%).
%). After the engine stops, the temperature of the cooling air rises to 13 or higher, and the electromagnetic clutch is turned on again, and the 9/Pressa Taniyari is driven at 20%.

As explained above, in the cooler system incorporating the oJ Henya compressor according to the present invention, the compressor can always be operated in a state commensurate with the cooling load.

Next, a control 1l that operates the solenoid pulp 101
The I(b) path will be explained using FIG.

In the figure, SWI is the main switch of the cooler system.
Turning on starts the circuit. T1゜Tt = T
s is a comparator, and the temperature of the thermistor (temperature 1) 601 is 1. , 1. , 1. It is configured to generate an on signal when: t, it,.

1, the setting value satisfies tl > tt > ts and can be changed by the Rable resistor Rj. First, if the thermistor temperature t is higher than tl, the comparators T, , T
, , l'.

Both are turned on, transistors Tr and ij are turned on, relay RF is turned on, 9 magnetic clutch 700 is operated, and the compressor is rotated. This Toki, Transistor'l
'rl @ 'l'rl is off and solenoid pulp 10
1 remains off and the compressor reaches 100% 00% capacity. Next, when the thermistor temperature t becomes tl>t>t, the comparators T and Fi turn off, and T turns on.
The transistor Tr is turned on, and the on-off signal of the oscillation circuit 602 is applied to the transistor Trl at 44, and the transistor Tr is turned on and off again according to the oscillation circuit 6020 signal. Therefore, the solenoid pulp 101 becomes in the FJjT connected state.Furthermore, when the thermistor temperature t decreases and becomes h > t > ts, both the comparators T+ and Ts are turned off, and the transistor 'i'rIij is turned on slowly, so that the solenoid pulp 1'01 to become energized.

The compressor capacity f is 20% capacity. thermistor ml
When ft becomes 1 (1s, comparator T3 turns off, so * I"y/ resistor Trs turns off and relay dy
To turn off the warehouse, the magnetic clutch 700 is disengaged and the rotation of the compressor is stopped.

In the embodiment of the present invention described above, the variable 48 control is performed by detecting the cooling temperature at the outlet of the evaporator of the cooler system, and nine examples have been shown. , co/pressor rotation speed, etc., or a combination thereof.

Further, the solenoid pulp may be operated to close the discharge groove when energized.

Further, in the above embodiment, the plunger 105 is used as a switching cell.
Alternatively, the cylindrical rotary pulp 110 as shown in FIGS. 8 and 9 may be controlled to rotate in the m direction in FIG. 1bJ.

Since the present invention has the above-mentioned structure and function, it is possible to adjust the capacity in three stages in the vane compressor. This has the effect of improving the cooling operating force E'eif in a continuous state commensurate with the cooling load, the operating feeling, and the cooling feeling.

Furthermore, since the compressor can be moved much smaller during startup, the electromagnetic clutch can be made smaller.

Also, since the number of on/off rotations is reduced, the durability of the electromagnetic clutch is improved.

[Brief explanation of drawings]

Figure 1 is a vertical cross-sectional view of one embodiment of the present invention, and is taken from 1f-1 in Figure 2.
Figure 2 shows the Wr direction along 11#lc, and Figure 2 is 1-1 in Figure 1.
FIG. Figure 3 (a), lbJ is an explanatory diagram showing the principle of variable capacity, Figure IN4 is an explanatory diagram showing the operation of the variable container, and Figure 5 is a cooler incorporating the device shown in Figures 1 and 2. An overall view of the system, Figure 6 is a diagram showing how the compressor capacity changes depending on the cooling air temperature and the passage of time during the operation of the equipment shown in Figures 1 and 2. Operation of the solenoid pulp in the device shown in Figure 2 t-
The control circuit diagram, Fig. 8, is an explanatory diagram of the operation of the 61f Tani Hitomi using a switching pushbutton of a different type from the switching box shown in Fig. 4, and Fig. 9 (aJtb)leJ is the a of Fig. 8. - a layer,
Discharge pressure groove and switching valve cut out at bb@ and cc-, respectively. It is a sectional view of a pilot tie. l...rotor, 2...vane, 3...liner, 4
...Drive side side grate, 5...Rear side side plate, 6...Front housing/g, 7...Rear housing, 100...cII transformation violet compressor, 101...Solenoid pulp, 102,102'
...School. 104.104'...Spool guide, 105...
Plunger, 105a, 105b...hole, 106-...
・Spring, 110...Rotary pulp, 200・
... Vertically d device, 300... Receiver, 400... Expansion box, 500... Evaporator, 600... Control circuit, 70
0...Magnetic clutch, Bp, Bp...Bypass port, Pd, Pd'...Discharge pressure groove, pp, pp
'...Pylon) Ceramic, Vd...Discharge pressure chamber, vh...
・Pressure holding chamber + Vs... Suction pressure chamber. 2 chambers for Vp river. Patent Applicant: Nippon Denso Co., Ltd. Nippon Denso Co., Ltd. Patent Attorney: Akira Yoiki, Patent Attorney, Oro Nishidate, Patent Attorney, Kyosuke Nakayama, Patent Attorney, Akira Yamaguchi, Patent Attorney, Figure 1, Figure 2, Bp 3 Figure 4 Figure 5 Figure 6 Figure 1 → T (time) Figure 7

Claims (1)

[Claims] Rotor, this low! A vane consisting of a vane that can slide in a slit formed inside, a side plate that clamps this liner and forms an operating space, and a crank that forms a suction pressure chamber and a discharge pressure chamber with this side plate. In the compressor. The side plate constituting the suction pressure chamber is provided with two bypass ports that communicate slowly with the working space and the suction pressure Mt, and spools are provided to open and close the bypass ports, respectively, and the two spools are connected to the discharge pressure chamber. In the communication groove that conducts the end face. A switching valve is provided that can be switched to three stages: communication between the discharge royal chamber and the two spool ends, communication between the discharge pressure chamber and one spool end surface, and communication between the discharge pressure chamber and the two spool end surfaces. A variable capacity compressor, characterized in that a solenoid pulp for operating the switching valve in three stages is provided in a groove communicating the switching valve and the discharge pressure chamber.