JPS623191A - Coolant compressor - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a refrigerant compressor used for cooling automobiles and the like.

Conventional Technology In recent years, there has been a strong demand for refrigerant compressors used for automobile air conditioning to control the discharge capacity of refrigerant gas according to the heat load in the vehicle interior, thereby saving energy and improving comfort. There is.

As a means of controlling the discharge capacity of refrigerant gas, an indirect method is generally used in which high-pressure gas is introduced by operating a solenoid valve and control is performed using this high-pressure gas (for example, "Mitsubishi Electric Report, Vol. 67, No. 5, pp. 6-8).

An example of the conventional refrigerant compressor mentioned above will be explained with reference to FIG.
, FIG. 4 shows a rolling piston type refrigerant compressor having two cylinders, in which a rolling piston 4 driven by a crankshaft 3 is disposed in a front cylinder 1 and a rear cylinder 2 having cylindrical inner walls. There is. The front cylinder 1 and the rear cylinder 2 are sealed on both sides by a front plate 6, a plate 6, and an intermediate plate 7. Reference numeral 8 denotes a front case, which is provided with an intake port 9, and is located between the front case 8 and the front plate 6, and between the front plate 6° and the front cylinder 1. A refrigerant gas suction passage 10 is formed in the intermediate plate 7 and the rear cylinder 2, and a front suction hole 11. Refrigerant gas is supplied from the rear suction hole 12. Further, a control valve 13 and a coil spring 14 for opening and closing the rear suction hole are installed in the suction flow passage 10 of the rear cylinder 2. 16 is an electromagnetic valve that controls high pressure gas that operates the control valve, and piston 16. Bi-spring 17. coil 18
゜The piston receiver is part 19. It consists of a high pressure gas passage, a pilot passage 21, and a bypass passage 22. In addition, 23 is a shell, 24 is a discharge port, and 25 is a clutch.

The operation of the refrigerant compressor configured as above will be described below. First, in the case of a bar load operation to control the cooling capacity, when the coil 18 of the solenoid valve 16 is energized, the piston 16 is attracted to the piston receiver 19, which blocks the bypass passage 22 and opens the high pressure gas passage 20. ,
The pressure inside the pilot passage 21 becomes high, and the control valve 14 is moved to the left, thereby blocking the rear suction hole 12. Therefore, the refrigerant gas supplied from the suction port is supplied from the suction passage 1° into the front cylinder 1 through the front suction hole 11, but the refrigerant gas supply into the rear cylinder 2 is stopped, and the refrigerant gas into the front cylinder 1 is stopped. will be operated only by

On the other hand, when operating at full load to achieve maximum cooling capacity,
When the coil 18 of the solenoid valve 15 is de-energized, the piston 1
6 uses a bias spring 17 to shut off the high pressure gas passage 20 and open the bias passage 22. At this time, the high pressure gas in the pilot passage 21 is transferred from the bypass passage 22 to the suction passage 1.
0, the pressure in the pilot passage becomes low, the control valve 13 is moved to the right by the coil spring 14, and the rear suction hole 12 is opened. Therefore, refrigerant gas is also supplied into the rear cylinder 2, and both the front cylinder 1 and the rear cylinder 2 are operated.

As described above, in order to control the discharge capacity, the conventional refrigerant compressor is configured to control high-pressure gas using a solenoid valve and indirectly operate the control valve.

Problems to be Solved by the Invention However, in the above configuration, in order to control the discharge volume, the control valve is operated indirectly by a solenoid valve via high-pressure gas, so the flow path is formed in a complicated manner. Moreover, since it has a dual structure of a control valve and a solenoid valve, it is difficult to achieve miniaturization.

Furthermore, since the solenoid valve operates by continuously supplying electricity to the coil, there is a problem in that heat is generated in the coil, which impairs its durability.

Furthermore, since high-pressure gas leaks to the low-pressure side, loss occurs and the efficiency of the refrigerant compressor decreases.

The reason why the conventional refrigerant compressor described above uses a configuration in which a control valve is operated indirectly by a solenoid valve to perform capacity control is as follows. In other words, a control valve requires a large amount of displacement to control its capacity, and since there is a pressure difference before and after the control valve, in order to directly operate the control valve with a solenoid valve, it is necessary to increase the suction force of the solenoid valve. It needs to be bigger. Therefore, the power consumption of the solenoid valve must be increased,
Heat generation increases during continuous energization. Therefore, in order to ensure the reliability of the solenoid valve, the solenoid valve itself has to be considerably enlarged, making it difficult to directly control the capacity using the solenoid valve.

54. As mentioned above, with the conventional configuration, not only is it difficult to achieve miniaturization, but it also causes deterioration of the solenoid valve.

This had the problem of reduced efficiency.

The present invention solves the above problems, and by controlling the capacity by directly driving the solenoid valve, it achieves miniaturization with a simple configuration, improves the reliability of the solenoid valve, saves energy, and improves efficiency. The present invention provides a refrigerant compressor with improved performance.゛Means for solving the problems In order to solve the above problems, the refrigerant compressor of the present invention includes a cylinder having a cylindrical inner surface, and a cylinder having a cylindrical inner surface.
6. A rotor disposed within the cylinder, a plurality of slits formed radially within the rotor, a plurality of vanes sliding within the slits, and a side plate closing the cylinder from both sides; An electromagnetic device that directly opens and closes two suction holes for supplying refrigerant gas into the cylinder and a refrigerant gas flow path leading to one of the suction holes by activating a movable iron core by applying pulse current. It is equipped with a valve.

Effects The effects of the above-described configuration of the present invention are as follows. That is, the movable iron core of the solenoid valve is attracted by pulsed energization and held by a permanent magnet. Further, when a pulse current is applied in a direction to demagnetize the permanent magnet, the movable iron core separates from the magnetic force of the permanent magnet. The movable iron core of this solenoid valve allows one of the two suction holes through which refrigerant gas is supplied into the cylinder.
Directly open and close the flow path to the suction hole at the location. In this way, when the flow path is open, sufficient refrigerant gas is supplied into the cylinder from the two suction holes, resulting in full-load operation that produces the maximum cooling capacity, and the flow path is closed. In this case, refrigerant gas is supplied from only one suction hole, resulting in part-load operation with controlled discharge capacity.

As a result, in order to operate the solenoid valve by pulse energization,
Because there is almost no heat generation and the amount of current can be increased,
The suction force increases, the amount of displacement of the movable iron core can be increased, and the capacity can be directly controlled. Moreover, since the control is performed within the flow path of the suction refrigerant gas, it is not affected by leakage of high-pressure gas.

EXAMPLE An example of the present invention will be described below with reference to FIGS. 1 to 3. In FIGS. 1 and 2, 26 is a cylinder having a cylindrical inner wall, and a rotor 27 is disposed inside. The rotor 27 has a radial slit 28 through which the page 729 slides. The cylinder 26 is closed on both sides by a front plate 30 and a rear plate 31. 32, a suction boat 33 is provided with a rad cover to the cylinder, and a suction chamber 34. A discharge chamber 35 is formed. The cylinder 26 has a first suction hole 3
6 is provided, and a second suction hole 37 is provided at the suction end point of the rear plate 31. A solenoid valve 39 is installed in a refrigerant gas flow path 38 leading from the suction chamber 34 to the second suction hole. The electromagnetic valve 39 includes a movable iron core 41 that slides within a sleeve 40, a piston 42 made of a non-magnetic material attached to the movable iron core 41, an iron core receiver 43, a permanent magnet 44, and a second side. It is composed of a coil 46, a secondary coil 46, a bias spring 47, an outer yoke 48, and a lower yoke 49. In addition, 6o is an intermediate plate, 61 is a discharge hole, 52 is a discharge valve, 63 is a discharge valve valve plate, 54 is a rear case, 66 is a discharge union, 66 is an oil separator, 57 is an oil control pulp, and 5th is a shaft , 69 is a clutch.

Capacity control of the refrigerant compressor configured as above will be explained. In FIG. 2, as the rotor 27 rotates, the front vane 29a reaches the second suction hole 37 provided at the suction end point in the cylinder blade chamber eo formed by the front vane 29a and the rear vane 29b. Until then, refrigerant gas is supplied from the first suction hole 36 provided in the cylinder 26. ``Then, until the rear vane 29b passes through the first suction hole 36, refrigerant gas is supplied from both the first suction hole 36 and the second suction hole 37, and then,
Until the rear vane 29b reaches the second suction hole 37, the refrigerant gas enters the cylinder blade chamber 6 only from the second suction hole 37.
o, and the suction stroke ends. this
At this time, if the refrigerant gas flow path 38 from the suction chamber 34 to the second suction hole 37 is blocked, the rear vane
□After 29b passes through the first suction hole 36, the second
In the section up to reaching the suction hole 37, the supply of refrigerant gas into the cylinder blade chamber 60 is stopped, and the capacity is controlled by the amount of refrigerant gas that is not supplied.

Next, the operation of the solenoid valve 39 installed in the refrigerant gas flow path 38 to the second suction hole 37 will be explained with reference to FIG. In Fig. 3 &, the refrigerant gas flow passage 38 is open, and the refrigerant gas is also injected from the second suction hole 37.
' □ Shows the state during full load operation when air is supplied to the vane chamber 60 and the maximum cooling capacity is achieved. This means that the negative side coil is energized in pulses, and the movable iron core 41 is moved to the iron core receiver 43.
After the magnet is attracted to the magnet and the current is turned off, it is held by the permanent magnet 44.

Next, when pulse current is applied to the secondary coil, the magnetic force of the permanent magnet 44 is demagnetized due to the reverse magnetic field, and the movable iron core 41 is separated from the iron core receiver 43 due to the spring force of the bias spring 47, and the piston FIG. 3 shows that the flow path 38 is blocked by 42. At this time, no refrigerant gas is supplied into the cylinder blade chamber 60 from the second suction hole 37, resulting in part-load operation where the capacity is controlled.

As described above, according to this embodiment, the movable iron core of the solenoid valve is energized to the primary and secondary coils with an instantaneous pulse, and the permanent magnet and bias spring can repeatedly attract, hold, and release. . Therefore, almost no heat generation occurs in the coil, and it becomes possible to increase the amount of current supplied and increase the attractive force. Therefore, since the amount of displacement of the movable iron core can be increased, the refrigerant gas flow path can be directly opened and closed, and capacity control can be performed with a simple configuration. Moreover, the solenoid valve itself can be miniaturized, and since it is pulse energized, there is almost no power consumption to operate the solenoid valve, which is useful for energy saving through capacity control.

Furthermore, since the suction refrigerant gas is directly controlled, there is no leakage loss of high-pressure gas, etc., and highly efficient capacity control can be performed.

In this embodiment, the movable iron core is sucked and held in a full load operation, but a similar configuration is also possible for a part load operation.

Effects of the Invention As described above, the present invention includes a cylinder having a cylindrical inner wall, a rotor disposed within the cylinder, a plurality of slits formed radially within the rotor, and a plurality of slits arranged inside the slit. A plurality of sliding vanes, a side plate that closes the cylinder from both sides, two suction holes for supplying refrigerant gas into the cylinder, and a refrigerant gas flow communicating with one of the suction holes. A movable iron core that directly opens and closes the flow path.

It is composed of a permanent magnet, a bias spring, and a solenoid valve consisting of a negative side and a secondary side coil.The movable iron core is actuated by pulse energization, and the capacity can be controlled, so the configuration is simple and the refrigerant compression In addition to making it possible to downsize the machine,
Its practical effects are extremely impressive, such as increasing the efficiency and reliability of capacity control and saving energy.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional view of a refrigerant compressor according to an embodiment of the present invention, FIG. 2 is a front sectional view of the same refrigerant compressor, and FIGS. 3 a and 3 b show the operation of a solenoid valve used in the refrigerant compressor. The explanatory diagram, FIG. 4, is a longitudinal sectional view of a conventional refrigerant compressor. 26...Cylinder, 27...Rotor,
29... Vane, 36... First suction hole, 37... Second suction hole, 38... Distribution path, 39...... Solenoid valve, 41...Movable iron core, 42...Piston, 44...Permanent magnet, 46...-Next coil 1.46...・
...Secondary coil, 47...Bias spring. Name of agent: Patent attorney Toshio Nakao and one other person? G
-・-Sirijita 27--11-ra! ? --1-n y6--Stick f class entry y7--Year 2' 511-5 Kuki 11j6 t4t--B"SuYn visit--&Subanishi 45-11-jo stop] Ral 4C --- 28 (soaking) Figure 2 Figure 3 Figure 4 δ

Claims (1)

[Claims] (1) a cylinder having a cylindrical inner wall, a rotor disposed within the cylinder, a plurality of slits formed radially within the rotor, a plurality of vanes sliding within the slits; It includes a side plate that closes the cylinder from both sides, two suction holes that supply refrigerant gas into the cylinder, and a solenoid valve that opens and closes a refrigerant gas flow path leading to one of the suction holes. , the solenoid valve includes a primary coil that attracts the movable iron core in the sleeve, a permanent magnet that holds the attracted movable iron core, a secondary coil that demagnetizes the magnetic force of the permanent magnet, and the movable iron core. A refrigerant compressor consisting of a bias spring that restores the core and a piston attached to the movable iron core.