JPS59145389A - Rolling piston type rotary compressor - Google Patents

Abstract

PURPOSE:To make a compressor miniature and lightweight, by providing a plurality of vanes and by making suction ports opened to one side face of a cylinder to increase the amount of displacement, and as well to aim at reducing vibration and noise, by reducing variations in the torque of a crank shaft and the maximum value of the same. CONSTITUTION:There are provided vanes 4, 9 press-contacted to the outer peripheral surface of a rolling piston 2, suction ports 16, 17 and discharge valves 8, 12, the suction ports 16, 17 being positioned in one side face of a cylinder in the part which is near to the center of the cylinder 3 inside of the inner diameter section of the cylinder 3 and being communicated with an intake passage which is not shown. With this arrangement, when a cylinder 3 chamber changes from 270 deg. at which the volume of the chamber is maximum, to 305 deg. by the rotation of a crank shaft 1 by 35 deg., the suction ports 16, 17 for refrigerant gas are blocked by a rolling piston 2 to restrain, at a minimum, the counterflow of refrigerant gas in the cylinder 3 chamber from the suction ports 16, 17 to the suction passage. As a result, the amount of displacement can be greately increased to make the compressor miniature and lightweight. Further, the maximum value in the torque of the crank shaft 1 may be made small in comparison with that of conventional compressors, and as well variations in the torque may be reduced, thereby the vibration and noise of the compressor may be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to improvements in rotary compressors, particularly rolling piston type rotary compressors for residential, commercial, and vehicle air conditioners.

FIG. 1 shows the compression mechanism of a conventional rolling piston type rotary compressor. In FIG. 1, l is a crankshaft driven by a motor or an engine, and is provided with an eccentric portion that rotates eccentrically in the direction of the arrow. A cylindrical rolling piston 2 is fitted into an eccentric portion of the crankshaft 1, and the rolling piston 2 is housed in a cylinder 3 so as to roll in contact with the inner circumferential surface of the cylinder 3. cylinder 3
A vane 4 is mounted so as to be constantly pressed against the outer peripheral surface of the rolling piston 2 by a spring 5. The refrigerant gas sucked into the cylinder 3 from the suction hole 6 provided in the cylinder 3 has a volume of the space surrounded by the vane 4, the rolling piston 2, and the cylinder 3.
It is compressed as it decreases with the rotation of the cylinder 3, and is discharged from the discharge hole 7 provided in the cylinder 3 into a housing (not shown) by opening the discharge valve 8.

Such a conventional rolling piston type rotary compressor discharges air once per revolution of the crankshaft. During this operation, the maximum torque applied to the crankshaft due to the pressure of the refrigerant gas is 300 to 400% of the average torque during one rotation, as shown by the broken line A in FIG. This large torque fluctuation causes large vibrations in the compressor, causing parts such as piping and the frame to vibrate, causing noise. Furthermore, hermetic compressors for air conditioners require motors with large starting torque. Furthermore, since the displacement amount is the same as the cylinder volume, it is difficult to downsize the compressor.

Therefore, it is conceivable to create a two-vane type with two sets of vanes, suction holes, and discharge valves, as shown in Figure 2, in which the same or corresponding parts as in Figure 1 are given the same reference numerals. Even if a two-vane type compressor is used, the torque fluctuation will be smaller, but the displacement will be the same as an L-vane type compressor with the same cylinder and rolling piston.

This invention was made in view of the above-mentioned circumstances, and an object of the present invention is to provide a rolling piston type rotary compressor that has a push force greater than the cylinder capacity, can be made smaller, and has small torque fluctuations. It is said that

That is, the present invention provides a rolling piston type rotary compressor comprising a cylinder, a crankshaft having an eccentric part that rotates eccentrically within the cylinder, and a cylindrical rolling piston fitted to the eccentric part of the crankshaft. , has at least two sets of vanes, suction holes and discharge valves that are in pressure contact with the outer peripheral surface of the rolling piston, and the suction holes are connected to the cylinder 9.
By providing it on the center side 1 from the cylinder inner diameter on the 111th surface,
This is designed to minimize the backflow of intake gas within the cylinder.

An embodiment of the present invention will be described below with reference to FIGS. 1 and 4.

An embodiment of the present invention shown in FIGS. 3 and 4 has two sets of vanes, suction holes, and discharge ports. In FIGS. 3 and 4, the same parts as in FIG. 1 are designated by the same reference numerals. In this embodiment, in addition to the conventional vane 4, spring 5, discharge hole 7, and discharge valve 8, the vane 9, spring 10, discharge hole 11, and discharge valve 12 are arranged point-symmetrically, as in the case of FIG. In addition, suction holes 16 and 17, which will be described later, are provided on the side surface of the cylinder 3 closer to the center than the cylinder inner diameter, and communicated with a suction passage (not shown). Third
In the figure, the cylinder chamber is divided into three parts: the cylinder chamber 13 is at its maximum capacity during the suction stroke, the cylinder chamber 14 is at 90° from the start of suction (suction capacity is 0), and the cylinder chamber 15 is at its maximum capacity during the suction stroke. This is the 90° state before the compression is completed. Further, FIG. 4 shows a state in which the crankshaft l (rolling piston 2) has rotated 35 degrees in the direction of the arrow, that is, clockwise, from the state shown in FIG. The suction hole 16 has the outer diameter dimension of the rolling piston 2 in the suction stroke in which the cylinder chamber reaches its maximum volume in FIG. 3, and the outer diameter dimension of the rolling piston 2 in the state shown in FIG. The vane 4 is formed into a half-sun-moon shape by a line close to the end surface, and the suction hole 17 is formed point-symmetrically with the suction hole 16. The relationship between the crankshaft rotation angle and the cylinder chamber volume of the two-vane compressor shown in FIG. The inside of the cylinder is divided into three chambers by the contact points of the two vanes and the rolling piston with the inner peripheral surface of the cylinder, and FIG. 6 shows the change in volume of one chamber.

FIG. 7 shows the change in cylinder chamber pressure in the case of FIG. 6. In the case where the suction hole is provided in the circumferential wall of the cylinder as shown in Fig. 2, the discharge valve opens when the pressure inside the cylinder exceeds the pressure in the discharge passage, and the pressure inside the cylinder does not rise during discharge. As shown by the solid line in FIG. 7, the suction hole is closed by the rolling piston only when the crankshaft rotation angle reaches 360°, the cylinder chamber is sealed, and compression begins. The maximum volume of the cylinder chamber occurs at a crankshaft rotation angle of 270°, and is larger than the displacement of a conventional single vane with the same cylinder and rolling piston dimensions, about 0.75 times, so the total displacement is about 1.5 times that of one vane. However, since there is no suction valve, while the crankshaft rotates from 270° to 360°, the refrigerant in one cylinder chamber is slightly compressed to a higher pressure than the refrigerant gas in the suction passage, causing the refrigerant to enter the cylinder chamber. The refrigerant gas returns through the suction hole.

Therefore, the rotation angle of this crankshaft is 270° to 360°.
Until then, no compression is performed, and the pressure within the cylinder chamber changes as shown by the solid line in FIG. On the other hand, in the embodiment of the present invention shown in FIGS. 3 and 4, the cylinder chamber has a maximum volume of 270° and an additional 35°.
When the crankshaft rotates to 305 degrees, the suction hole is blocked by the rolling piston, so the refrigerant gas in the cylinder chamber does not return from the suction hole to the suction passage. Therefore, compression starts, and the pressure change in the cylinder chamber at this time is the seventh
The result will be as shown by the broken line in the figure. Furthermore, the torque acting on the crankshaft shown in FIG. 2 is K as shown by the chain line B in FIG. It will look like C.

As mentioned above, one embodiment of the present invention has a two-vane shape as shown in FIGS. 3 and 4, and has a suction hole on the side of the cylinder to connect to the suction passage at the beginning of the compression stroke. 5K is designed to minimize the backflow of gas, so with a compressor with the same cylinder and rolling piston, the displacement can be approximately 1.4 times that of the conventional one, making the compressor more compact and compact. It can be made into a light lid. Further, as shown in FIG. 5, the embodiment of the present invention can make the maximum value of the crankshaft torque even smaller than that of FIG. 2, and the minimum torque value is positive, causing torque fluctuation becomes smaller, and therefore the vibration and noise of the compressor can be reduced.

In addition, in this invention, although the suction hole in the above-mentioned embodiment was in the shape of a half-round sun-moon, a plurality of round holes may be arranged in the same place. In addition, in this invention, although the above-mentioned embodiment has a two-vane type, it may be three or more vanes. In this case, the suction hole is based on the outer diameter of the rolling piston when the cylinder chamber has the maximum volume. From that point on, it should be provided within the area of the cylinder side that the rolling piston closes while the crankshaft rotates, or within the area of this area K (1° or more). As explained above, this invention has a plurality of vanes, and by opening the suction hole on the side of the cylinder, the displacement can be made larger than the cylinder chamber volume, making it compact and lightweight. This has the effect of reducing crankshaft torque fluctuations and the maximum torque value, and reducing vibration and noise.

[Brief Description of the Drawings] Figure 1 is a cross-sectional view of the compression mechanism of a conventional rolling piston type rotary compressor, and Figure 2 is a cross-sectional view of a conventional rolling piston type rotary compressor.
FIG. 3 is a cross-sectional view of a compression mechanism showing a vane type rolling piston rotary compressor; FIG. 4 is a cross-sectional view of a compression mechanism showing a rolling piston rotary compressor according to an embodiment of the present invention; is a cross-sectional view of the compression mechanism in a state where the crankshaft has advanced 35 degrees from the state shown in FIG. 3, FIG. 5 is a diagram showing changes in torque with respect to the crankshaft rotation angle, and FIG.
The figure shows the change in cylinder chamber volume with respect to the crankshaft rotation angle, and FIG. 7 shows the change in cylinder chamber pressure with respect to the crankshaft rotation angle. l...Crankshaft, 2...Rolling piston, 3...Cylinder, 4,9...
・Vane, 5.10...Spring, 6...
Inhalation hole? , II...Discharge hole, 8.12...
...Discharge valve, 13.14.15...Cylinder chamber, 16.17...Suction hole. Note that the same reference numerals in the figures indicate the same or corresponding parts. Agent Makoto Kuzuno - (1 other person) t 1 Fig. 6 2nd cause 4 Fig. t 6 Fig. O 6 Fig. &) 〉／Wandering map ＾

Claims (2)

[Claims] (1) In a rolling piston type rotary compressor that includes a cylinder, a crankshaft having an eccentric part that rotates eccentrically within the cylinder, and a cylindrical rolling piston fitted to the eccentric part of the crankshaft, the rolling piston The number of vanes, suction holes and discharge valves that are in pressure contact with the outer circumferential surface is reduced (
A rolling piston type rotary compressor, characterized in that it has two sets of both, and the suction hole is provided on the side surface of the cylinder closer to the center than the inner diameter of the cylinder. (2) Based on the outer diameter of the rolling piston when the cylinder chamber reaches its maximum volume, 13! f (n - number of vanes) The rolling piston type rotary according to claim 1, wherein the suction hole is provided within the area on the cylinder side that is closed by the rolling piston while the crankshaft rotates, or so as to span this area. compressor.