JPS59147895A - Multicylinder rotary type compressor - Google Patents

Abstract

PURPOSE:To make the capacity of a compressor controllable at will, by installing a shaft coupling having an annular or coillike detachable function made of a form-memory alloy in each of crank connecting parts of a multicylinder rotary compressor. CONSTITUTION:A shaft end part 4b of a main crankshaft 4 and a shaft end part 10b of an auxiliary crankshaft 10 are adjoined with each other in a state of being opposed face-to-face. At both these shaft end parts 4b and 10b, an annular coupling 16 made of a form-memory alloy in installed there, making up a shaft coupling element 29. The shaft coupling 16 has large clamping allowance at an optional temperature, while at other temperatures, its inner diameter comes small and is so designed as to couple these shaft coupling parts 4b and 10b as one body, so that when each one is heated or cooled, the capacity of a compressor can be controlled at will.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to a multi-cylinder rotary compressor in which a plurality of compression elements are vertically stacked.

[Prior art]

In order to control the capacity of a conventional double-borrowed rotary compressor, an arbitrary number of compression elements among all the compression elements are operated under no load by closing the suction side and not allowing refrigerant to flow into the compressor. However, since this compression element that operates without load is placed in a high-pressure sealed container and is under stress, high-pressure refrigerant gas leaks into the low-pressure cylinder of the compression element, causing eccentric rotation within the cylinder. The rollers and vanes exert a slight compression effect, resulting in the inconvenience of wasted input. Furthermore, since these compression elements that perform no-load operation 7 have sliding parts such as bearings, rollers, vanes, etc., power loss due to friction caused by these sliding parts is unavoidable. That is, in this type of compressor, even during no-load operation, a considerably large amount of wasted input is consumed, and the compression performance during capacity control operation is poor.

[Purpose of the invention]

The present invention has been made in view of the general situation of the prior art, and its purpose is to eliminate the above-mentioned drawbacks of the prior art, improve compression performance during capacity control operation, and save power. It is an object of each company to provide a multiple cylinder rotary compressor capable of fal control.

[A chest of inventions]

In other words, in order to fully control the capacity of the compressor, the present invention provides at least one compressor disposed on the same axis as the crankshaft of the main compression element, which always operates synchronously when the motor is operating.
An annular or coiled shape-memory alloy shaft joint having a function of connecting or disconnecting is attached to the opposing shaft ends of each of the two auxiliary compression elements with the crankshafts, extending over an equal length between each of the two crankshafts. With this configuration, the shaft joint made of memory alloy is heated to expand the shaft joint, thereby increasing its inner diameter and creating a gap between the two crankshafts. The shaft joint tightens the two crankshafts and connects the two crankshafts by stopping the heating of the splintered shaft joint and cooling it to reduce the size of the shaft joint. In other words, by connecting both crankshafts, the auxiliary compression element can operate in synchronization with the raw compression element, or by disconnecting both crankshafts, the operation of the auxiliary compression element can be stopped, and the capacity of the compressor can be adjusted as desired. can be controlled in multiple stages.

[Embodiments of the invention]

Hereinafter, embodiments of the present invention will be described based on all the drawings. 1st
The figure is a longitudinal sectional view of a multi-cylinder rotary compressor according to a first embodiment of the present invention. In this figure, a two-cylinder rotary compressor having two cylinders is shown for ease of explanation. However, it goes without saying that this embodiment can be similarly applied to a multi-cylinder rotary compressor having six or more cylinders arranged in a stacked manner on the same axis (see Figs. 2 to 6). (same as well).

In FIG. 1, 1 is an airtight container, and inside the airtight container 1, there is a motor 2, which is an electric element, in the upper part, and a main compression element 3 and an auxiliary compression element 9, which are directly connected to the motor 2 in the lower part, are located between them. It is arranged and housed via the shaft coupling element 29. The main compression element 3 is composed of the following parts. That is, the cylinder 6, the king crankshaft having the eccentric portion 4α, and the cylinder 6
A roller 5 that rotates eccentrically by an eccentric portion 4α of the main crankshaft 4, a vane (not shown) that comes into contact with the roller 5 and divides the inside of the cylinder 6 into a high pressure chamber and a low pressure chamber, and an upper opening of the cylinder 6. an upper end face plate 7 which closes the lower opening of the cylinder 6 and has a bearing part 7α of the main crankshaft 4; and a lower end face plate 8 which closes the lower opening of the cylinder 6 and has a bearing part 8α of the main crank l1i1114.
It is.

′-! In addition, the auxiliary compression element 9 is similarly composed of the following parts. That is, the cylinder 12, the auxiliary crankshaft 10 having an eccentric portion 10af, the roller 11 eccentrically rotated within the cylinder 12 by the eccentric portion 10α of the auxiliary crankshaft 10,
A vane (not shown) that abuts the roller 11 and divides the inside of the cylinder 12 into a high pressure chamber and a low pressure chamber, an upper end face plate 13 that closes the upper opening of the cylinder 12 and has the entire bearing portion 13α of the auxiliary crankshaft 10; This is a lower end face plate 14 that closes the lower opening of the cylinder 12 and has a bearing portion 14α for the auxiliary crankshaft 10.

The main compression element 3 and the auxiliary compression element 9 are the lower end face plate 8 of the former.
It is fixed in a predetermined position by fitting with the cylindrical portion 13h of the latter upper end face plate 13.

Note that the lower end face plate 8 and the upper end face plate 13 form a hollow portion 1 between the sealed walls in which the shaft coupling element 29 is housed.
5 is composed. In the hollow portion 15, the shaft end 4b of the main crankshaft 4 and the shaft end 10b of the auxiliary crankshaft 10 are adjacent to each other and face each other as shown. At these opposing shaft ends 4h and 10b, an annular shaft joint 16 made of a shape memory alloy (hereinafter referred to as memory alloy) is attached to l1.
It is attached to each of the II ends 4h and 10h over an equal length, and the shaft joint 16 connects the shaft joint element 29.
is configured. This memory alloy shaft joint 16 is connected to the main crank [1ill1] which has the same inner diameter at any temperature.
4 and the shaft end 10h of the auxiliary crankshaft 10. γ
In terms of crystallinity, the shaft joint 16 is shrunk to have a smaller inner diameter, and the shaft end portions 4b and 10h are fully tightened to integrally connect the main crankshaft 4 and the auxiliary crankshaft 10.

The operation of connecting and disconnecting the main crankshaft 4 and the auxiliary crankshaft 10 using the shaft joint 16 will be described in detail later.

Next, I will explain the thread path through which the refrigerant gas flows in the frozen cycle.
I will clarify. 24 is a suction pipe of the main compression element 3, and 25 is a suction pipe of the auxiliary compression element 9. That is, gas flowing from a heat exchanger (not shown) constituting the refrigeration cycle device through the suction pipe 24 is compressed by the main compression element 3 to become a high-temperature, high-pressure gas, and the high-temperature, high-pressure gas flows through the discharge port 18. via valve 19
' and a valve holder 20. It is discharged from the hollow part 15. Similarly, the gas flowing from the heat exchanger through the suction pipe 25 is compressed in the auxiliary compression device 19 and becomes high temperature and high pressure. It is discharged from the valve 22 into the hollow part 15. The hollow part 15--These discharged gases are shown in the arrow a
As shown, the air passes through the entire passage 17 of the cylinder 6 of the main compression element 3 and exits to the upper part of the enclosed container 1, and from the discharge pipe 26 of the compressor to each external refrigeration cycle device (not shown). Flowing sequentially b〈.

In the two-cylinder rotary compressor configured as described above, the operation of the shaft coupling element 29 directly related to the present invention will be explained. In FIG. 1, the main crankshaft 4 and the auxiliary crankshaft 10 are connected by a shaft coupling 16 of a shaft coupling element 29. In FIG. The manner in which the power from the main crankshaft 4 is transmitted to the auxiliary crankshaft 10 will be fully explained below.

The main crankshaft 4 rotated by the energized motor 2,
The movable part of the main compression element 3 is driven to compress the refrigerant gas sucked in from the suction port 24, and the high temperature and high pressure refrigerant gas is discharged from the discharge pipe 18 through the discharge valve 19 into the hollow part 15.

Here, as shown in the figure, the shaft end 4b of the main crankshaft 4 and the shaft end 10b of the auxiliary crankshaft 10 are connected by a shaft joint 16 made of a memory alloy whose shape, ie, inner diameter, does not change at any temperature at this time. Therefore, the auxiliary crankshaft 10 rotates together with the main crankshaft 4. Therefore, the auxiliary crankshaft 10, which rotates once, fully drives the movable part of the auxiliary compression element 9, compresses the refrigerant gas sucked in from the suction port 25, and releases the high temperature and high pressure refrigerant gas to the discharge pipe 2.
1 to the hollow portion 15 through the entire discharge valve 22.

At this time, the shaft joint 16 made of a memory alloy provided in the hollow part is exposed to these high temperature and high pressure refrigerant gases, but the transformation mixture layer of the memory alloy, which has been set in advance, is not reached. The crankshaft 4 and the auxiliary crankshaft 10 are still connected together by the shaft joint 16, so that both the earth pressure m-element 3 and the auxiliary compression element 9 perform a compression action.

Next, the operation of separating the main crank +1illI4 and the auxiliary crankshaft 10 by the shaft coupling element 29 will be explained.

FIG. 2 is a longitudinal sectional view showing a state in which the main crank 4ilI14 and the auxiliary crankshaft 10 are separated from each other in the two-cylinder rotary compressor shown in FIG.

In other words, compared to the state in which both shafts are connected as shown in Fig. 1, an overload is applied to the refrigeration cycle.
The discharge pressure of the compressor has increased, and the temperature of the discharged gas from each compression element is high. That is, in the compressor shown in FIG. 2, the temperature of the discharged gas exceeds a preset arbitrary temperature that causes transformation of the memory alloy forming the entire shaft joint 16. The inner diameter of the shaft joint 16 expands. Therefore, the inner wall of the shaft joint 16, the end portion 4h of the main crankshaft 4, and the auxiliary crankshaft 1
The shape returns to the original memorized shape in which there is a gap 27 between the shaft end 10b and the outer wall of the shaft end 10b. As a result, the connection between the king crank 11illI4 and the auxiliary crankshaft 10 is disconnected, the 11 force of the main crankshaft 4 is no longer transmitted to the auxiliary crankshaft 10, and the compression action of the auxiliary compression element 9 is stopped.

That is, if this shaft disconnection function is applied to the operation of the refrigeration cycle, when the heating capacity becomes excessive, the operation of the auxiliary compression element 9 can be stopped and the operation can be reduced to an appropriate heating capacity.

As is clear from the above explanation, the connection foot of the shaft coupling 16 is
The disconnection operation at the time of overload makes it possible to control the capacity of the compressor to two stages in total.

However, in the configuration of the first embodiment shown in FIG.
It lacks functionality to allow for flexible control.

In order to achieve all of this object, the second embodiment of the present invention is described in the sixth embodiment.
As shown in the figure. FIG. 3 is a longitudinal sectional view similar to FIG. 1, and the same reference numerals indicate the same parts having the same functions (the same applies to other drawings).

In the second embodiment shown in this figure, a heater 28 is arranged to electrically heat the annular shaft joint 16 made of a memory alloy with a slight gap between the heater 28 and the outer periphery of the shaft joint 16. Note that the connection operation of the shaft coupling element 29 in this embodiment is completely the same as in the first embodiment, so a complete explanation will be omitted. Therefore, only the disconnection operation of the shaft coupling element 29 will be described.

In other words, in a refrigeration cycle device that performs cooling or heating operation, if the cooling capacity or heating capacity becomes excessive and these capacities are lowered, a signal is sent to the compressor from a control device (not shown) that selects and controls all of the operating modes. is emitted.

This signal energizes the heater 28 of the compressor, and the heater 28 heats the memory alloy shaft joint 16 adjacent thereto. When the temperature at which the memory alloy undergoes transformation is reached by this heating, the shaft joint 16 expands and its inner diameter becomes large. A gap 27' (+-) is created between the shaft end IQA of the shaft 10 and the outer wall.
The communication between the main crankshaft 4 and the auxiliary crankshaft 10 is removed, and the compression action of the auxiliary pressure m element 9 is stopped.

In addition, when the main crankshaft 4 and the auxiliary crankshaft 10 are to be connected again, the heater 28 is activated by a signal from the control device.
energization is stopped, and the heating action of the heater 28 is stopped.

Then, the temperature of the shaft joint 16 decreases due to heat radiation, and this temperature drop causes the shaft joint 16 to return to its memorized shape at a low temperature.

Thereby, the main crankshaft 4 and the auxiliary crankshaft 10 are connected.

That is, in this second embodiment, the main crankshaft 4 and the auxiliary crankshaft 10 are freely connected and disconnected by the heating action of the memory alloy shaft joint 16 by the heater 28.

FIG. 4 is a longitudinal sectional view similar to FIGS. 1 to 3, showing a fifth embodiment of the present invention. In the third embodiment shown in FIG. 4, the annular memory alloy shaft coupling 16 is the first. This embodiment is similar to the second embodiment, but the means for connecting and disconnecting the shaft joint 16 is different. That is, in the second embodiment, the means was a heater, but in this embodiment,
Piping 35 communicating with the hollow part 15 and the low pressure side of the refrigeration cycle
．． 37 and pipes 36 and 38 communicating with the high pressure side are provided, and low temperature, low pressure or high temperature and high pressure refrigerant is passed through these pipes, and the shape of the shaft coupling 16 is changed due to stiffness.
It connects and disconnects shafts. 31.32.
33, 34 are solenoid valves that control the flow of fluid through pipes 35, 36, 37, 38, respectively.

In the compressor of the fifth embodiment having such a configuration, the main crankshaft 4 and the auxiliary crankshaft 10 are connected by the shaft joint 16 in the following manner. In other words, the solenoid valve 32
, 311, open the solenoid valves 31 and 33, and open the shaft coupling 1.
The hollow portion 15 provided in No. 6 and the low pressure side pipes 35 and 37 of the refrigeration cycle are communicated via the inlet pipe 30 and the outlet pipe. As a result, the low-temperature, low-pressure refrigerant of the refrigeration cycle flows into the hollow portion 15 along the thread path indicated by the solid arrow. In this way, the shaft joint 16 is shrunk by the low-temperature refrigerant, returns to its low-temperature shape, and its inner diameter becomes smaller, thereby connecting both crankshafts.

Conversely, the separation between the main crankshaft 4 and the auxiliary crankshaft 10 is as follows. In other words, close the solenoid valves 31 and 33,
Solenoid valve 32, 3. Open the hollow part 15, the high pressure side pipes 36 and 38 of the refrigeration cycle, the inlet pipe 60 and the outlet pipe 3.
9. As a result, the high-temperature, high-pressure cold tofu of the refrigeration cycle goes to the middle 9 section 15 along the thread path shown by the broken line arrow C! ′
#Neru. In this way, the shaft joint 16 is heated by the high-temperature refrigerant, and the shaft joint 16 expands and the inner diameter of the shaft joint 7 becomes larger. As a result, a gap is created between the shaft joint 16 and the main crankshaft 4 and the auxiliary crankshaft 10, allowing them to be separated. will be held.

By following the above operating procedure, both crankshafts can be freely connected and disconnected 7, and the capacity of the compressor can be freely controlled to two stages in total.

FIG. 5 is a longitudinal sectional view similar to FIGS. 1 to 4, showing a fourth embodiment of the present invention. In the two-cylinder rotary compressors of the first to sixth embodiments described above, the shaft coupling 1
6 was annular in shape, but in this embodiment, the shaft coupling 40 has a coil shape as shown in FIG. Therefore, in this embodiment, since the shaft joint 40 is coiled, when the inner diameter becomes smaller, the shaft end 4h of the crankshaft 4 is tightened by the frictional force generated as the inner diameter becomes smaller. and m end u of the auxiliary crankshaft 10
3h can be firmly connected. In other words, since the structure is simple and the tightening force is large, manufacturing costs can be reduced.

Note that the operation of connecting and disconnecting the king crankshaft 4 and the auxiliary crankshaft 10 in this embodiment is the same as in the above-described embodiment, so a description thereof will be omitted.

〔Effect of the invention〕

As explained above, the multiple cylinder rotary compressor of the present invention is provided with an annular or coiled shaft joint made of a memory alloy that connects the shaft ends of the crankshafts of each compression element. By fully heating or cooling the shaft joint and changing its inner diameter, the two shafts can be freely connected and disconnected, so the capacity of the compressor can be adjusted as needed.
k It can be operated freely by dividing it into any number of stages. Therefore, it is possible to eliminate wasteful compression action in the auxiliary compression element and power loss due to friction in the sliding parts, thereby significantly reducing the input power, improving the compression performance of the compressor and contributing to power saving. Further, as described above, the shaft joint structure is simple, and there is no need for special processing to connect the raw crankshaft and the auxiliary crankshaft, so manufacturing costs can be extremely reduced. As described above, the effects of the present invention are remarkable.

[Brief explanation of drawings]

FIG. 1 is a longitudinal cross-sectional view of a two-cylinder rotary compressor according to the first embodiment of the present invention, and FIG. 2 is a diagram showing the two-cylinder rotary compressor shown in FIG. FIGS. 3 to 5 are longitudinal sectional views of two-cylinder rotary compressors according to second to fourth embodiments of the present invention, respectively. 2...Motor 3...Soil compaction element 4.
... King crankshaft Ah, 10h ... Shaft end 5.
11...Roller 6, 12...Cylinder 7
．． 13... Upper end face plate (cylinder end face plate) 8.14...
・Lower end face plate (cylinder end face plate) 9...Auxiliary compression element
10... Auxiliary crankshaft 15... Middle 9 section (between sealed walls) 16, 4Q... Shaft joint 28... Heater
31.32.3434 ...Solenoid valve 35, 34
37.38...Piping sentry 1 A armpit? V 37 Figure 4

Claims (1)

[Scope of Claims] (In a multi-cylinder rotary compressor in which 11 main compression elements and at least one auxiliary compression element are vertically stacked, each of the compression elements has a crankshaft on the same axis. 7%, the mutually opposing shaft ends of the crankshafts are adjacent to each other, and an annular or coil-shaped shaft joint made of a shape memory alloy is attached to the connecting portion of each crankshaft. Cylinder rotary compressor. (2) A sealed space is provided between the compression elements, the shaft coupling is provided in the sealed space, and a heater is disposed near the shaft coupling. A multi-cylinder rotary compressor according to claim 1. (3) A sealed gap is provided between the front sF compression elements, the shaft joint is located within the sealed nitrogen gap, and the shaft joint is located within the sealed nitrogen gap. A multi-cylinder rotary compressor according to claim 1, further comprising a pipe communicating with a closed space and through which high-temperature and low-temperature refrigerants flow, and fC solenoid valves provided at the inlet and outlet of the pipe.