JPS60162087A - Capacity-control type compressor - Google Patents

Abstract

PURPOSE:To facilitate temperature control and the control for engine load by applying the voltage signal for designating a compression capacity, onto a solenoid valve for opening and closing a communication hole to a crank chamber and an intake chamber. CONSTITUTION:In order to capacity-control a swash-plate type compressor which is used for a car, etc. and driven by an engine, each detected output of an inside-air temperature sensor 76, outside-air temperature sensor 77, intake pressure sensor 78, etc. is input into a microcomputer 79, and comparison-calculated with the signal of a temperature setting device 91. Said output is input as compression-capacity designating signal Va into a comparator 73, and the signal Va is corrected by the signals supplied from an accelerator switch 92, and an overheat switch 93, and said signal Va is compared with the signal Vb of a triangular- wave generator 74 in a certain frequency, and the pulse signals having a pulse width corresponding to the compression capacity designation signal are output to opening/closing-control a solenoid valve 44.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field] The present invention relates to a swash plate type compressor in which a piston is reciprocated by the rotation of a swash plate disposed in a crank chamber, and particularly relates to control of its compression capacity.

[Prior art]

In conventional swash plate compressors, in order to make the compression capacity variable, the swash plate is provided with a variable inclination angle, and by changing the inclination angle of the swash plate, the stroke of the piston can be changed from zero to maximum load. ing. In order to control the angle of inclination of the swash plate, a communication hole is provided to connect the crank chamber and suction chamber.

A valve operated by a refrigerant-filled bellows is installed to open and close this communication hole, and the pressure difference between the crank chamber and the suction chamber is measured by the valve opening gauge. It is now possible to do so.

Now, when the valve is fully open, there is no pressure difference between the crank chamber and the suction chamber, so the compression reaction force acting on the piston is applied to the swash plate, and the angle of inclination of the swash plate becomes maximum. The piston reaches its maximum stroke.

Conversely, when the valve is closed, the pressure in the crankshaft increases due to blow pie gas, and back pressure acts on the piston.
The angle of inclination of the swash plate becomes small and the piston stroke becomes almost zero.

Therefore, if the refrigerant sealing pressure in the bellows is set somewhat higher than the pressure in the suction chamber when the temperature of the refrigerant evaporator reaches 0°C, for example, the temperature of the evaporator will be much higher than 0°C. At this time, the suction side pressure is higher than the bellows internal pressure, so the valve opens, the angle of inclination of the swash plate increases, and the compression capacity increases. In this state, when the temperature of the evaporator approaches 0° C., the suction pressure decreases, and as a result, the angle of inclination of the swash plate becomes small, and the compression capacity becomes minimum.

In the above-mentioned compressor, the compression capacity can be automatically changed according to changes in the refrigerant load of the compressor.
Therefore, it is only possible to control the temperature to maintain it at a preset temperature, and it is not possible to control the capacity by 1.5 times depending on other conditions.

Therefore, the capacity control type swash plate combination leaf described in item 1 is used as a refrigerant compressor for an automobile air conditioner.

When driving on/non-vehicle 9 For example, when you want to obtain high output such as during overtaking acceleration, or when you want to reduce heat dissipation from the air conditioner's condenser when the temperature of the cooling water rises abnormally, use the compressor, It is not possible to control the compression capacity of

[Purpose of the invention]

It is an object of the present invention to provide a capacity control type compressor device that can adjust the compression capacity to a desired level by applying capacity control signals according to two types of conditions.

Another object of the present invention is to provide a capacity control type compressor which has a simple structure and high reliability in capacity control.

[Structure of the invention]

Is this invention 1d clan? A swash plate type compressor in which a piston is reciprocated by the rotation of a swash plate disposed indoors, the swash plate being provided with a variable angle, and communicating between the crank chamber and the suction chamber. A hole and a solenoid valve for opening and closing the communication hole are provided, and the swash plate angle changes depending on the difference in pressure between the crank chamber and the suction chamber when the solenoid valve is in an open state and a closed state. This is a variable capacity compressor with variable compression capacity.

A solenoid valve drive circuit that drives the above-mentioned solenoid valve, and a duty-northern variant of the duty-cycle generator that generates the gas at a constant frequency, and the duty ratio is determined according to the input compression capacity designation signal. This is a capacity control type compressor device having a control pulse generation circuit that outputs a variable pulse signal as a control signal for the electromagnetic valve drive circuit.

Here, an example of the above-mentioned control/gurus generation circuit includes a triangular wave generator that generates a triangular wave of a constant frequency,
The output wave of the triangular wave generator is compared with the voltage value of the compression capacity designation signal, and an ie of a width corresponding to the compression capacity designation signal is determined.
It consists of a comparator that outputs a pulse signal.

〔Example〕

Two embodiments of the present invention will be described below with reference to two drawings.

First, an embodiment of a variable capacity compressor used in the present invention will be described with reference to FIG.

A cylinder bore 2a is provided at one end of the cylinder casing 1.
A cylinder block 2 is formed, and the opening at the other end has a through hole 3 into which the main shaft 4 is inserted.
A front housing 3 into which a radial bearing 5 for rotatably supporting the main shaft 4 is press-fitted is arranged and fixed in the through hole 3aVcI''i.

A main shaft 4 is located at the outer end of the through hole 3a of the front housing 3.
A main shaft lead-out cylinder 3b that protrudes so as to contain the main shaft is provided,
A mechanical run rule 7 is disposed with a seal chamber 6 in the space formed by the main shaft 4 and the inner wall of the main shaft lead-out cylinder 3b. A crank chamber 1a is formed between the inner wall of the front housing 3 and one end of the 7-liner block 2, and a rotor 8 is fitted into the side end of the main shaft 4 within the crank chamber la.

The rotor 8 includes a plate body 81 that is fitted onto a side end of the main shaft 4 and has an arm 82 at one end, and is rotatably supported by the end of the arm 82 and rotated around the rotation center axis of the main shaft 40. It is constituted by a slope portion 30 that is sloped. Furthermore, a protrusion 301 is provided at the end of the slope portion 30 toward the plate 81.

A hook-shaped stopper portion 302 is provided at the end of the protrusion 301 . Further, the plate body 81 is provided with a slide l'a 811 corresponding to the protrusion 301.

At the upper end of the slide groove 811 there is a hook-shaped strike part 8.
12 are provided. The protrusion 301 is slidably disposed within the slider groove 43, and the storage grooves 302 and 81.2 of the upper unit define the sliding range of the protrusion 301, so that the slope of the slope 30 is The angle changes within a predetermined range.

Next, a ball bearing 50 is press-fitted into the inside of the two-ring-shaped rocking plate 9, and a sleeve 60 having a flange 61 at one end is press-fitted into the inside of this goal bearing 50. The other end of the sleeve 60 is screwed into the center of the sloped portion 30 so that the sleeve 60 is located at the center of the sloped portion 30. At this time, a slight gap is formed between the slope portion 30 and the rocking plate 9, and the thrust race 26 is attached to the slope portion 30 and the rocking plate 9 near the outer periphery of the slope portion 30.
A thrust needle bearing 25 is sandwiched between the thrust race 26 and the thrust race 26. A thrust race 26 is similarly arranged between the inner wall surface of the front housing 3 and the plate 81, and a thrust needle bearing 25 is sandwiched between the thrust races 26.

On one end surface of the slope portion 30, a one-way rack 3 is provided opposite to the plate body 81.
5 is provided, and a washer 3 is also provided on one end surface of the swing plate 9.
5 is provided. And the washer 35 of the slope part 30
A coil spring 34 is installed parallel to the main shaft 4 between the washer 35 of the swing plate 9 and the snap ring 36 fitted onto the main shaft 4.

The other end of the main shaft 4 is rotatably supported in the Linder Pro 2 by a radial bearing 37, and a thrust needle bearing 38 disposed on the end surface of the main shaft 4.
and is rotatably supported by an adjustment screw 39 via a plate spring 4o.

Furthermore, an ear shaft 41 protruding toward the cylinder casing 1 is provided at the end of the swing plate 9.

The cylinder casing 1 is provided with a slider groove 43 corresponding to the ear shaft 41, and the ear shaft 41 is provided with a cylindrical slider 42.
is disposed within the slider groove 43 so as to be slidable through the slider groove 43 .

Further, one end of a piston port -14 is rotatably supported on the surface of the swing plate 9, and the other end of the piston rod 4 is connected to a piston I5 disposed within the cylinder bore 2a.

cylinder) 1′? A suction hole 71 for sucking fluid and a discharge hole 72 for discharging fluid are bored in one end surface of the housing 2a. A valve plate 1 with a suction valve and a discharge valve connected to control fluid flow to the discharge hole 72
6 to the cylinder block 2 via the gasket 17 and to the cylinder having the partition wall 18a, y, ? The valve plate 1 is inserted into the cylinder through the gasket 21 so that a suction chamber 19 and a discharge chamber 20 are formed by the valve plate 18.
6, the valve plate 16 and the cylinder head 1
8 is fixed onto the cylinder blower 2 with bolts 22, and the cylinder casing 1 is closed.

Further, the suction chamber 19 and the crank chamber 1a communicate with each other through a communication hole 45, and the communication hole 45 is controlled to open and close by a solenoid valve 44. The communication hole 45 is a radial connection hole that connects the communication hole portion 451 and the communication hole portion 452 and communication hole portions 451 and 452 that are bored in the cylinder casing I below the communication hole portion 451. (not shown). The valve part 441 of the solenoid valve 44 is inserted into the connection hole, and the solenoid valve 44 is turned on and off.

The valve portion 441 slides within the connecting hole and substantially controls the opening and closing of the communicating hole 45. Note that since the solenoid valve 44 is tightly attached by the snap 443, fluid will not leak through the gap between the valve portion 441 and the connecting hole.

When the main shaft 4 is given two rotational motion by an engine or the like, the rotational motion is transmitted to the rotor 8 fitted to the main shaft 4, and this rotational motion is further transmitted to the rocking plate 9 disposed on the inclined surface.
is transmitted to. However.

The ear shaft 41 attached to the swing plate 9 is connected to the slider groove 4.
3, the movement of the rocking plate 9 relative to the direction of rotation of the rotor 8 is smoothed out, and the rotational movement transmitted to the rocking plate 9 by the rotor 8 is.

The rotation of the slope portion 30 is converted into a rocking motion.

When the rocker 9 swings, the piston 15 reciprocates via the piston rod 14 connected to the rocker plate 9.
Taking fluid from the suction chamber 19 and compressing this fluid,
It is being discharged into the discharge die 20.

When the solenoid valve 44 is open, the suction chamber 19 and the crank chamber 1a are in communication with each other through the communication hole 45, so that the pressures in the suction chamber 19 and the crank chamber are equal. At this time, the slope portion 30 of the rotor 8 has a maximum angle (main shaft 4
The reference point is the state perpendicular to . ) is adjusted by the coil gune 34. therefore,
Piston 15 becomes the stroke of war. (At this time, the so-called normal compression ratio is achieved.) When the solenoid valve 44 is closed, the communication hole 45 that communicates the suction chamber 19 and the crank chamber 1a is blocked, so that the gap between the piston 15 and the cylinder bore 2a is closed. From then on, the blow pipe gas in the compression process flows into the crank chamber 1a, and the pressure in the crank chamber 1a increases. Therefore, the inclination angle of the slope portion 3o gradually becomes smaller, and the piston stroke becomes smaller.

However, if the angle of inclination becomes too small, the movement of the piston 15 will be almost gone, eventually the movement of the fluid will stop, and the movement of the lubricating oil will also stop.

Therefore, the protrusion 3 provided at the storage portion 812 of the slide groove 811 provided in the plate body 81 and the slope portion 30
01 strike, by Gube 3Q2.

The angle of inclination of the slope portion 30 is maintained within a certain range.

Note that the minimum angle of the slope portion 3o is determined to be 10 to 20% of the compression ratio at the maximum angle.

Next, with reference to FIGS. 2 to 5, a control section for controlling the capacity of the above-mentioned variable capacity compressor will be explained.

Now, in the variable displacement compressor solenoid valve 44 shown in FIG.
The communication hole 45 is repeatedly opened and closed at a constant cycle of a waveform as shown in FIG. Here, if the pulse interval is t2, the rate at which the communicating holes 45 are open within a certain time (hereinafter referred to as data ratio DR) is expressed by the 9th equation (1). is given by

1°DR=□・・・・・・(1) t, +t2 When DR=O, that is, j,==Q, that is, when the Noculus current is not applied to the solenoid valve 44, the communication hole 45 is completely closed. It is in a closed state. At this time, the piston 15 operates at its maximum stroke. That is, maximum compression capacity is obtained. On the other hand, when p DR=1, that is, 12=00, that is, solenoid valve 4
4, the communication hole 45 is fully open.

At this time, the piston operates with a minimum stroke. That is, it has the minimum compression capacity. DR is Gurus width 1 + To.
e Since any value between 0 and 1 can be taken by changing the pulse interval t2, the duty ratio of the pulse current applied to the solenoid valve 44 (expressed by the same formula as equation (1)) By controlling this, the time-averaged opening of the communication hole 45 can be controlled to an arbitrary value. This means that the piston stroke can be varied arbitrarily between maximum and minimum.

FIG. 3 is a block diagram showing a circuit configuration of an embodiment of a control section that actually performs capacity control according to the above principle.

Referring to FIG. 3, the comparator 73 compares the input compression capacity designation signal V with the output triangular wave Vb of the triangular wave excavator 74, and determines the width of the curve according to the capacity designation signal. This is a circuit that outputs a pulse signal. The output of the comparator 73 is applied to the solenoid valve drive circuit 75, and the solenoid valve drive circuit 7
5 corresponds to the output signal of the comparator 73. For driving/
A positive current is applied to the solenoid valve 44.

Referring to FIG. 4, from the triangular wave oscillator 74, FIG.
) is output as a triangular wave (■) as shown by a solid line, and if the compression capacity designation signal va applied to the comparator 73 is also a voltage signal shown as a solid line in FIG. The output of the device 73 is a pulse signal as shown in FIG. 4(b). If the period of the triangular wave is T and the width of the signal output from the comparator 73 is tl, then the duty ratio is as follows.

It is expressed as t, /T. This pulse is given to the solenoid valve drive circuit 75, and from the solenoid valve drive circuit 75 the solenoid valve 4
The drive current applied to the drive currents 4 and 4 is controlled to have the same waveform. Therefore, the communication hole 45.

It will be released at oR=t+/T.

Next, when the compression capacity designation signal changes from Va to the high voltage signal V' shown by the dashed line in FIG. like,
The pulse width becomes narrow (t,')/Grus waveform.

Therefore, its data ratio is t,'/T. Here, since t,)t,', the time-average opening amount of the communication hole 45 becomes small.

Therefore, the compression capacity can be arbitrarily controlled by simply inputting a signal corresponding to the required pressure line capacity to the comparator 73.

Returning again to FIG. 3, an example will be described in which the above-described capacity-controlled compressor device is used in a compressor for an air conditioner of an automobile to control temperature.

The detection outputs of two various sensors for temperature control, such as the inside air temperature sensor 76, the outside temperature sensor 77, and the suction pressure sensor 78, are input to the microcomputer 79, and the set temperature information of the temperature setting switch 91 is also input. The detection signals from the three sensors 76 to 78 are inputted to the microcomputer 79 according to the preset dimensions, h, and tanogram.

The required compression capacity is calculated from the setting information from the temperature setting switch 91, and a corresponding voltage signal is output. By inputting this voltage signal to the comparator 73 as a compression capacity designation signal, it is possible to control the two compression capacities and perform temperature control. The temperature control in this case has the advantage that it does not require the connection/disconnection of an electromagnetic clutch unlike the temperature control in conventional automobile air conditioners.

Also, during sudden acceleration or when the engine overheats, the engine load cannot be reduced.

A) An accelerator switch + 92 to detect the depression of the accelerator pedal of a car and a switch 93 to detect overheating of the engine are provided, and the detection signal is used to obtain a voltage signal indicating the minimum compression capacity (or O), and this is sent to the comparator. 73 as a compression capacity designation signal, the engine load can be reduced in the case of sudden acceleration or overheating; , a capacity control type concrete that can obtain the required compression capacity simply by applying a pressure signal that specifies the compression capacity.

A device is obtained. Because it can easily control the compression capacity according to various conditions and demands.

It has the advantage of making it possible to easily control the temperature of an air conditioner, especially an air conditioner for an automobile, and the engine load.

[Brief explanation of the drawing]

Fig. 1 is a cross-sectional view of a rocking type compressor according to the present invention, and Fig. 2 is a cross-sectional view of the rocking type compressor according to the present invention. Figure 3 is a block diagram for generating the waveform signal for controlling the solenoid valve used in the floating compressor according to the present invention, and Figure 4 is a block diagram for generating the waveform signal generated by Figure 3. FIG. 2 is a waveform diagram showing reference voltage formation and threshold voltage for generating a Nockles signal and a Nockles signal. 1... Cylinder casing, 2... Ring block, 3... Front handle, 4... Main shaft, 5...
・Lasoal bearing, 6... Seal chamber, 7... Mechanical knob, 8... Rotor, 9... Rocking plate, I4
...Piston rod, 15-piston, 16...valve plate. 18.../ring head, 19... suction chamber, 20...
・Discharge chamber, 44...Solenoid valve, 45...Communication hole, 71
...Suction hole, 72...Discharge hole, 73...Comparator,
74... Triangular wave oscillator, 75... Solenoid valve, drive circuit. Agent (7127) J: , '171 l L:,
Yosuke Procedural Amendment 1 Indication of the case 1982 Patent Application No. 16089 2, Name of the invention Person making the amendment Relationship to the case Patent applicant Telephone number (0270) 24-1211 Name (184) Sanden Co., Ltd. 4 Order for amendment date of publication 5 Description subject to amendment (Detailed explanation of the invention column) 6 In the 14th page, line 12 of the description of the contents of the amendment, “operates at the maximum stroke, i.e. maximum” is changed to “minimum stroke” In other words, it is corrected to ``with the minimum stroke.'' In the 16th line of the same page, ``It operates with the minimum stroke.In other words, the minimum'' is corrected to ``with the minimum stroke.'' In other words, it is corrected as "maximum".

Claims (1)

[Claims] ] A swash plate type compressor in which a screwdriver is reciprocated by rotation of a swash plate disposed in a crank chamber, the swash plate being provided with a variable angle. In addition, a communication hole connecting the crank chamber and the suction chamber and a solenoid valve that opens and closes the communication hole are provided. a variable capacity compressor in which the compression capacity is changed by changing the swash plate angle depending on the difference in the pressure difference between the two; a solenoid valve drive circuit that drives the solenoid valve; and a duty circuit that generates pulses at a constant frequency. A control/gurus generation circuit that is a northern modified gurus generator and outputs a gurus signal whose duty ratio changes according to an input compression capacity designation signal as a control signal for the electromagnetic valve drive circuit. A capacity control type compressor device having. 2. In the capacity-controlled compressor device according to claim 1, the control/surge generating circuit comprises: A triangular wave generator that generates a triangular wave with a constant frequency. It is characterized by comprising a comparator that compares the output wave of the triangular wave generator with the voltage value of the compression capacity designation signal and outputs a Grus direct code having a width corresponding to the compression capacity designation signal. Capacity control type compressor equipment.