JPS5874884A - 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] Regarding a compressor such as a compressor, specifically, the mechanism is simplified by making the injection gas passage, which is an element of the capacity increase mechanism, and the capacity control passage, which is an element of the capacity reduction mechanism, common. The purpose of this invention is to prevent chattering of the control valves provided in relation to both the passages.

In a compressor used in a refrigeration system, such as a rotary compressor, a capacity control boat and an injection boat are opened at predetermined positions facing a closed space in a cylinder chamber under a compression process,
Compressors whose compression capacity can be controlled in two stages have recently come into widespread use.

Refrigeration equipment is a device that undergoes rapid load fluctuations, so when the load becomes large, intermediate-pressure gas refrigerant is sent into the cylinder chamber from the injection boat to increase the compressor output by increasing the density of the compressed gas. When the load is small, the VC uses a capacity control boat to form a circuit that communicates the space in the cylinder chamber for the compression process with the suction side for a certain period of time, thereby delaying the start of compression and reducing the compressor output. The conventional capacity control mechanism of this type is divided into a common boat system in which both the boats are common, and an individual boat system in which the injection gas passage and the capacity control passage are each independent and become the next system. There are three methods: a passage method and a common passage method in which both the passages are common.

The first common boat system uses a compressor having the structure shown in FIGS. A) is activated to block the piston valve (hole (211) through which the intermediate pressure gas is injected from the piston valve (20i), and the output is increased, while the intermediate pressure gas is supplied By cutting off the piston row and moving the piston row far away from the common boat (A) by elastic force, the output can be reduced by connecting the bypass passage 0? 〇In this common boat method, since one hole is shared, it is impossible to set the hole diameter and position to maximize both the increase and decrease in capacity. The second individual passage system has the compressor structure shown in Figure 3 as an element, and since each passage has an independent passage, it is suitable for increasing and decreasing output. However, the bypass passage (1 key and capacity control bow) (the piping system for opening and closing the control valve α inserted between 91' and the injection bow) This method requires two piping systems, one for sending intermediate-pressure gas, and has the disadvantage of increasing the number of parts and raising manufacturing costs.

The third common passage method, as shown in Figs. 4 and 5, is that an injection boat is provided in communication with the passage (end) to which intermediate pressure is applied when the output increases and suction pressure is applied when the output decreases. , Ben CI! The element is a compressor having a structure in which it communicates with the chamber (1) connected to the passage (goods) through Although the structure has been simplified,
During operation under reduced capacity, every time the cylinder chamber communicating with the injection boat αQOI' undergoes a process changeover from suction to compression, compressed gas flows back into the injection boat QOI' and opens the cylinder chamber. Disadvantage is that the valve (C) is pressed down, causing the valve (C) to chatter and generate vibration noise, which is an inconvenient force that leads to noise.

In addition, the injection boat (capacity control boat when operating under increased output to inject intermediate pressure gas from one boat) (
Since 91' is left open, refrigerant gas flows into the space of the valve seat section (1) and (j), which reduces the compression capacity and efficiency. In view of the fact that rotary compressors according to
In particular, in a compressor in which a capacity control boat and an injection boat are provided facing a closed space where pressure increases in the compression process, an injection gas passage communicating with the injection boat;
A bypass passage communicating with the suction passage; a control passage capable of communicating with a gas region having an intermediate pressure lower than the discharge pressure and higher than the suction pressure; and a front chamber of the cylinder chamber that slidably accommodates the piston valve. A control valve is provided that communicates with the boat and applies elastic force to the piston valve in a direction away from the capacity control boat, and the injection boat is connected to the front chamber when the piston valve retreats. Furthermore, when moving forward, it is connected to the striking cylinder chamber which can be communicated with the control passage to form a companion configuration.

DESCRIPTION OF THE PREFERRED EMBODIMENTS In order to clarify the specific contents of the present invention, a rolling piston type rotary compressor as an example shown in the accompanying drawings will be described in detail below.

In Fig. 6, (l) is a cylinder, which has a cylinder chamber (1→ ) with a circular horizontal cross section in the center, and the cylinder is press-fitted into the cylindrical casing (2) and welded at key points. This makes it fixed.

A circular roller (4) eccentrically attached to the rotating shaft (3) is housed in the cylinder chamber (1a), and is provided so as to be able to rotate while slidingly contacting the peripheral wall of the cylinder chamber (1a). .

The cylinder (1) is provided with a suction passage (5) that opens into the cylinder chamber (la) and a blade chamber (6), and is slidably fitted into the blade chamber (6). The blade (7) faces into the cylinder chamber (la) so as to be in contact with the circumferential surface of the rotor (4), and although not shown, an ammunition is interposed on the back side of the blade (7),
8 By introducing discharge pressure into the blade chamber (6), a high-pressure region similar to that of the inner surrounding air of the casing (1) is created, and by doing so, the tip of the blade (7) is brought into elastic contact with the roller (4). Press so that the cylinder chamber (
1a) is divided into two chambers by this blade (7): a low pressure chamber communicating with the suction passage (5) and a high pressure chamber communicating with a discharge passage provided in a float head (not shown).

The configuration described above is a well-known structure related to a general rolling piston type rotary compressor. control boat (9) and jet boat) QO
I, an injection gas passage 0D, a bypass passage (121) communicating with the suction passage (5), a control passage (131), and a control valve α4, respectively.On the other hand, the cylinder (1) is provided with a casing ( A passage (+81) is provided which passes through the passage 2) in an airtight manner and opens to the outside, and which communicates with the control passage 03).

The capacity control boat (9 and injection boat 00) is a capacity control boat (9) located on the upper side near the suction passage (5) based on the direction of revolution of the roller (4), and a cylinder chamber (1a). Openings are made at predetermined positions on the surface forming the wall of the cylinder chamber (Xa), facing the closed space where the pressure increases in the compression process. In addition, both boats (6), α
The front and back of Q is not necessarily limited to the above-mentioned arrangement, and depending on design conditions, the front and back may be reversed.

The injection gas passage 0υ is a passage for communicating between the injection boat QO) and the control valve 0υ, and is installed in the rear head (8), but this is considerably larger than the bypass passage (121). Form into a narrow passage.

Bypass passage (121) A hollow passage formed in an arc shape in the burr head (8), and which is a hollow passage formed in the cylinder chamber (1a).
The end openings facing the two are connected to the suction passageway (5) at a position facing each other, and the other end is connected to the control valve 04.

The control passage (131) is a passage for communicating the passage a& with the control valve Q41, and is formed in the rear head (8).

Next, the control valve 0 set is placed in a cylindrical chamber QS formed in the rear head (8) facing the capacity control boat (9).
By accommodating the piston valve part to which elastic force is applied in the direction away from the capacity control boat (9) by the coil spring aη, a front chamber facing the capacity control boat (9) with the piston valve (161 as the boundary) It is a piston type control valve that is partitioned into a rear chamber on the opposite side and a rear chamber on the opposite side, and is an important element in performing capacity control for increasing and decreasing output.

This control valve Ql is configured such that when the piston valve t1e is pushed down against elastic force, the valve portion at the tip closes the capacity control boat (9).

The end of the bypass passage α2 is connected to the control valve I so as to open to the lower side wall of the cylinder chamber a9, so that the bypass passages a and a are always connected to the cylinder chamber Q51 regardless of the position of the piston valve aQ. It communicates with the front room.

Furthermore, the control passage (131) is connected to open to the upper side wall of the cylinder chamber 09, so that the passage 03 always communicates with the rear chamber of the cylinder chamber 09 regardless of the position of the piston valve (16). I'm doing it.

Further, the injection gas passage aυ is connected to open to the side wall of the intermediate portion of the cylinder chamber θ9, and the passage 0υ is switched to communicate with the front chamber or the rear chamber of the cylinder chamber 051 depending on the position of the piston valve aO. There is.

That is, by setting the connection position of this injection gas passage (II) to a predetermined position, when the piston valve Oe retreats, the passage Qllf communicates with the front chamber, and when it moves forward, it communicates with the rear chamber. Therefore, it is essential that such switching communication be performed.

The mode of capacity control operation of the compressor configured as described above will be explained next. When the load of the refrigeration system using the compressor as the drive source is light and the capacity control operation is performed, the passage (I
Valve a9 connected outside IIOK Cousing (2) is closed to prevent intermediate pressure gas refrigerant from being sent into control passage 03.

As a result, the pressure in the rear chamber in the cylinder chamber 09 decreases, and the piston valve +161 is pushed up in the direction away from the capacity control boat (9) by the elastic force, and as a result, As shown, the capacity control boat (91, injection boat 00) and the bypass passage α2 are connected to the cylinder chamber (151,
communicated by the antechamber of.

Therefore, in the trench where the surface of the roller (4) that slides against the rear head (8) passes through the capacity control boat (9), the sealed space in the cylinder chamber (l a) is connected to the suction side by the bypass passage α2. A7! IX will be completed.

Note that until the partition part passes through the capacity control bow) (91 and then the injection bow) (101), the injection gas passage aυ and the cylinder chamber (19) make the inner space of the cylinder chamber (1a) into the bypass passage α2. However, the injection gas passage aυ is narrow and has a large fluid resistance, and the pressure rise in the cylinder chamber (1a) until the partition reaches the injection bow fill, for example, Side pressure 5ζ
Since the amount of gas flowing backward through the injection bow) (101) is approximately 1.0 to 2.0-2. Therefore, a predetermined capacity control operation determined by the position of the boat αC and the hole diameter is stably performed.

In this case, the rear chamber, which serves as a back pressure chamber for the piston valve αe, communicates only with the sealed control passage (131) and there is no pressure fluctuation. While the piston valve (161) is being pushed up to the extreme position and performing capacity control operation, the piston valve (161) does not vibrate due to heat, so there is no risk of abnormal noise being generated.

On the other hand, when the load on the refrigeration system increases and it becomes necessary to increase the compressor output, the forefertilizer valve 09 is opened and the control passage Q
A gas refrigerant at an intermediate pressure, for example 12 to 13Y4, is fed into 31.

As a result, the pressure in the rear chamber in the cylinder chamber 051 increases, and back pressure that overcomes the elasticity of the fill spring (17) is applied to the piston valve QO. is pushed down and the valve tip is moved to the capacity control boat (
9) is in a closed state, and the space of the cylinder chamber na) and the bypass passage Q2+ are completely cut off, while the injection gas passage 0υ communicates with the control passage c131 through the rear chamber.

Therefore, the intermediate pressure gas refrigerant is injected depending on the pressure difference between the cylinder chamber (l→inner space pressure at that time, e.g. 0.6~7.0''!A and the fluid resistance of the gas passage 0υ). Since an appropriate amount of refrigerant is injected into the cylinder chamber CXa from lω, the refrigerant gas having a high density is compressed and the output is increased.

In this case, since the piston valve αe directly closes the capacity control boat (9), there is no dead space that would reduce compression efficiency, and efficient compression operation is performed.

Although the present invention has been explained above using a rolling piston type rotary compressor, the present invention can be applied to a sliding vane type rotary compressor or a reciprocating compressor in the same manner. It is possible to configure a compressor with capacity control.

As is clear from the above description of the present invention, since the capacity control boat (9) and the injection boat (Ql) are provided independently, it is possible to select any hole diameter position for each. , an optimal design for effectively increasing or decreasing output is possible.

Furthermore, by providing the capacity control boat (9) and the injection boat (101) in connection with the control valve α, it becomes possible to share the bypass and injection passages, and therefore the The piping system is simplified and costs are reduced due to a reduction in the number of parts.

In addition, the only thing that acts as back pressure on the piston valve (161) in the control valve (14) is the intermediate pressure gas used for operation, and the cylinder chamber (161) during the capacity control operation is
1a) Since it is constructed so as not to be affected by the pressure in the valve, chattering of the valve can be reliably prevented and noise generation can be eliminated.

Furthermore, the present invention can easily convert a standard constant capacity compressor into a capacity controlled compressor by simply replacing the rear head (8) by providing each element necessary for a mechanism for increasing or decreasing capacity in the rear head (8). There is also the advantage that it can be changed to

[Brief explanation of the drawing]

Figures 1 and 2 are a plan view of the main parts of a conventional common boat type compressor and a front view of the main parts shown in reverse. Figure 3 is a plan view of the main parts of a conventional individual passage type compressor. FIG. 5 is a plan view and front view of the main parts of a conventional common passage type compressor, FIG. 6 is a plan view of the main parts of an example of the compressor of the present invention, and FIG. 7 is a front view of the main parts shown in reverse. Indicates capacity increase operation status. FIG. 8 is a front view of the main parts shown in reverse, similar to FIG. 7, and shows a reduced capacity operating state. 〇(1)...Cylinder, (la)...Cylinder chamber. (4)...Roller, (5)...Suction passage. (6)...Blade chamber, (7)...Blade. (8)...Rear head, (9)...Capacity control boat. α [...Injection boat, aυ...Injection gas passage. Q21... Bypass passage, (13)... Control passage. (+4)... Control valve, (151... Cylinder chamber. (16)... Piston valve. Figure 1 Figure 2

Claims (1)

[Claims] l In a compressor in which a capacity control boat (9) and an injection boat 0α0 are provided facing a closed space where the pressure increases in the compression process of the cylinder chamber (1a), an injection gas passage αυ communicating with the injection boat Ol is provided. , a bypass passage (121) that communicates with the gIk person passage (5), a dual-purpose passage αJ that can communicate with a gas region with an intermediate pressure lower than the discharge pressure and higher than the suction pressure, and a □ sliding piston valve (16). The capacity control boat (9
) and is provided with a control valve I configured to communicate with the piston valve 08 and apply elastic force in a direction away from the capacity control boat (9), and the injection boat QOI is connected to the piston valve 0D The cylindrical chamber 09 is connected to the front chamber when the vehicle is moved backward, and to the control passage α4 when the vehicle is moved forward.
A compressor characterized by being connected to.