JPS6176786A - Rotary vane type compressor for cooling and refrigerating - Google Patents

Abstract

PURPOSE:To ensure sufficient suction of low pressure refrigerant into compressor while to reduce the size by arranging the suction port for low pressure refrigerant in the rotary direction of vane while splitting into two and providing check valves at said suction ports. CONSTITUTION:The suction port for low pressure refrigerant is splitted into rear suction port 11a and front suction port 11b which are arranged in the rotary direction of a vane 40 while check valves 60 are provided at said ports 11a, 11b. At first, the suction port 11a will open to a working chamber 41a through rotation of vane 40 to lead in low pressure refrigerant. Here, the suction port 11b is opening to the front chamber 41d but the check valve 60 will block the high pressure refrigerant from flowing into the rear chamber 41a. Upon further rotation of vane 40, the suction port 11b will also open to the rear working chamber 41a thus to suck the low pressure refrigerant through two suction ports 11a, 11b into the working chamber 41a. Consequently, sufficient supply of low pressure refrigerant into compressor is ensured while the size is reduced.

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention has a suction port for a low-pressure refrigerant and a suction port for a high-pressure refrigerant. This rotary vane compressor is designed to suck in refrigerant, and is suitable for cooling and freezing equipment in which refrigerant is circulated through a single compression evaporator between a refrigerating and freezing evaporator and a cooling evaporator. It is something.

[Prior Art] As is well known in the art, rotary vane compression molding consists of a main body having a cylinder bore, a rotor rotatably mounted in the main body, and a main body mounted in a vane groove of the rotor so as to be openable. and a vane that cooperates with the rotor to form a working chamber, and suction and compression of fluid is performed by changing the volume of the working chamber as the vane rotates due to rotation of the rotor.

By the way, in a cooling evaporator, the refrigerant is kept at a relatively high pressure (for example, 2
On the other hand, in refrigerating and freezing evaporators, the evaporation pressure of the refrigerant is low (for example, 1, 2
kg/cm2).

Therefore, in Japanese Patent Application No. 58-155899, the present applicant previously proposed that when a single rotary vane type compression unit is used for both cooling and refrigeration, two independent suction ports are provided in the compressor, and the compressor is By configuring Bit so that the low-pressure refrigerant suction port opens to the action chamber at the early stage of each suction process, and the high-pressure refrigerant suction port opens to the surrounding cloth at the latter stage of the suction process, refrigerating and freezing is possible. It was proposed that a low-pressure refrigerant for air conditioning and a high-pressure refrigerant for air conditioning can both be sucked into the same working chamber during the suction stroke due to the pressure difference between them.

[Problem that the invention seeks to solve]

In the rotary vane compressor configured as above, the dimension (size) of the low-pressure refrigerant suction port in the direction of rotation of the vane is the width (thickness dimension) of the vane in the same direction.
If the suction port is made larger than that, there will be a moment when the suction port communicates with both the NRF side working chamber and the rear side working chamber of the vane at the same time. At this time, the front working chamber is in communication with the high-pressure refrigerant suction port and is sucking high-pressure refrigerant, so the pressure is higher than that of the rear working chamber, so a portion of the high-pressure refrigerant in the front working chamber is Otherwise, the refrigerant will leak into the working chamber on the rear side through the low-pressure refrigerant suction port that spans the front and rear of the vane.

Therefore, in order to prevent such leakage from occurring, there is a restriction that the dimension of the low-pressure refrigerant suction port at a3 in the direction of rotation of the vane cannot be larger than the thickness of the vane, and due to this restriction, There is a problem in that the amount of low-pressure refrigerant flowing into the action chamber (suction amount) during the suction stroke is not sufficient.

Means for Solving Problem C] In order to solve this problem, in the rotary vane type compressor of the present invention, the suction port for low-pressure refrigerant is divided into two parts and these parts are arranged side by side in the direction of rotation of the vane. In addition, a check valve is provided at each of these separate low-pressure refrigerant suction ports.

[Function] The expression [divided into two]-I used in this specification does not mean to divide the area of one low-pressure refrigerant inlet into two, but to mean to divide the area of one low-pressure refrigerant inlet into two. It means "to set up". Since these two low-pressure refrigerant suction ports are arranged side by side in the rotational direction of the vane, as the vane rotates, the rear low-pressure refrigerant suction port first enters the initial stage of the suction process. A low pressure refrigerant is introduced into the working chamber. At this time, the front low-pressure refrigerant suction port opens into the front working chamber of the vane (the working chamber where high-pressure refrigerant is being sucked), or there is a check valve, so the high-pressure refrigerant flows into the rear working chamber. does not flow. When the vane rotates further, the front low-pressure refrigerant suction port also opens into the rear action chamber, so from then on, low-pressure refrigerant will be sucked into this action chamber from the two low-pressure refrigerant suction ports. . In this way, compared to the case where low-pressure refrigerant is sucked into the working chamber from one low-pressure refrigerant suction port, two
If suction is made from two low-pressure refrigerant suction ports, the amount of suction will increase significantly, so it is necessary to reduce the amount of low-pressure refrigerant into the compressor. 'i'7 IB, inhalation 111 fully (IT
``It has the effect of being able to keep the refrigeration and freezing evaporators sufficiently operational.

Furthermore, in the rotary vane compressor of the present invention, both low-pressure refrigerant and high-pressure refrigerant are sucked into the same working chamber and compressed. This has the advantage that it can be made smaller than a rotary compressor with the same discharge capacity that is configured to perform compression. In other words, in the latter type of compressor, the working chamber is divided into two parts, and only low-pressure refrigerant is sucked into one half and compressed.
The discharge amount is very small, and even if you combine this with the discharge amount of the high-pressure refrigerant compressed and discharged from the other chambers, the total discharge amount is smaller than the discharge amount from one working chamber of the present invention. Therefore, it is necessary to increase the size of the compressor accordingly.Compared to this, the compressor of the present invention has the advantage of being small but having a large discharge capacity.

[Example] FIG. 6 is a diagram schematically showing a refrigeration cycle using the rotary vane compressor 1. ff1? ;tl
l is a single discharge boat 10 and a low pressure refrigerant suction boat 11
and a high-pressure refrigerant suction boat 12.

The refrigerant coming out of the discharge boat 10 is condensed in a condenser 15 and then enters a gas-liquid separator 16. A cooling circuit 17 including a cooling evaporator 18 is connected to the liquid refrigerant outlet 16a of the gas-liquid separator 16.
and a refrigeration/refrigeration circuit 21 having a refrigeration/refrigeration evaporator 20 are connected in parallel, and the downstream ends of the cooling circuit 17 and the refrigeration/refrigeration circuit 21 are connected to a high-pressure refrigerant suction boat 12 and a low-pressure refrigerant suction boat 11, respectively. There is. The cooling circuit 17 includes an air conditioning expansion valve 19 provided upstream of the cooling evaporator 18.
The expansion valve 19 is a temperature-type automatic expansion valve that controls the evaporation pressure of the refrigerant in the evaporator 18 by the action of a temperature-sensitive tube 19a installed on the outlet side of the evaporator 18. The refrigeration/freezing circuit 21 includes a constant pressure expansion valve 22 provided upstream of the evaporator 20 and a check valve 23 provided downstream of the evaporator 20. The refrigerant pipeline downstream of the evaporator 18 in the cooling circuit 17 and the refrigerant pipeline downstream of the check valve 23 in the refrigeration/refrigeration circuit 21 are connected to a connecting pipe 2 having an electromagnetic shutoff valve 25 in the middle.
Connected by 4.

The expansion valve 19 of the cooling circuit 17 lowers the evaporator temperature to O in order to prevent frosting from occurring on the fins of the evaporator 18.
The evaporation pressure of the refrigerant is set to be relatively high, for example, about 2.0 kQ/ctr2, so as not to drop below about In order to provide ice-making capacity to the refrigerant, the evaporation pressure of the refrigerant is kept fairly low, e.g.
(+/Cl is set to about 112. Therefore, the high pressure and low pressure refrigerant suction ports 12.1 of the compressor 1
1 has 2. Oko/cm2 and 1,2 kr
The refrigerant gas returns at a pressure of +/cm2.

Note that the provision of the solenoid valve 25 is not directly related to the gist of the present invention, so a description of the action of the solenoid valve 25 will be omitted.

Next, an embodiment of the rotary vane type compressor according to the present invention will be described with reference to FIGS. 1 to 5d. Compressor 1
is a through-vane compressor in this example, and its structure will be explained with reference to FIGS. 7 housings 36 are axially aligned as shown and bolted together to form the main body of the compressor. A large-diameter portion 38a of a rotor 38 is rotatably mounted in the cylinder housing 34 in a centered manner, and boss portions 38b and 38c at both ends of the large-diameter portion 38a are formed on the inner surfaces of the front and rear end plates 32, 35. circular recess 32a.

35a so as to be rotatable. Shaft portions 38d and 38a protrude from these boss portions 381) and 38C on both sides and are rotatably supported by bearings provided at the center of the front and rear end plates 32.35. An extension part 38 extends from the outer end of the shaft part 38d through the inside of the front housing 30, and a boob as shown in FIG. It is designed to rotate.

As shown in FIG. 1, 1) the low-pressure refrigerant suction port 11 indicated by l'1' is attached to the outer peripheral wall of the fluorocarbon mill end plate 32; As can be seen from FIGS. 1 and 3, two holes 11a are formed along the outer flat surface of the periphery of the recess 32a of the end plate 32.

11b is bored and communicates with the low pressure refrigerant suction port 11 via two passages 11c and 11d extending radially within the end plate. These two holes 11a and 11b will be referred to as the "rear low-pressure refrigerant suction port J" and the "front low-pressure refrigerant suction port", respectively, when viewed in the rotational direction of the rotor 38.

The front end plate 32 has a suction port 1 for high-pressure refrigerant.
2a is also formed. The high-pressure refrigerant suction boat 1-12 is attached to the outer peripheral wall of the housing 30 to the front housing 30 (not shown), and this suction boat 12 is connected to the suction port through a suction chamber 12b formed in the front housing 30. It is in constant communication with 12a.

As is clear from FIG. 1 and FIGS. 5a to 5d, two vane grooves are provided in the large diameter portion 38a of the rotor 38 in the diametrical direction thereof, and are perpendicular to each other. A through vane 40, which is longer than the rotor's large diameter section 38a, is slidably arranged in the cylinder housing 3 with its both ends protruding from the outer peripheral surface of the rotor's large diameter section 38a.
It is in sliding contact with the inner peripheral surface of the cylinder bore in 2. As described above, since the large diameter portion 38a of the rotor 38 is eccentrically arranged in the cylinder bore, when the rotor 38 rotates in the direction of the arrow, the through vane 40 also rotates and one end of the through vane 40 rotates, causing one end of the through vane 40 to rotate in the direction of the arrow. It gradually protrudes from the outer peripheral surface, and the other end gradually retracts into the rotor large diameter section 38a. With this (14 configuration), the front and rear end plates 32
．． 35, cylinder housing 34, rotor large diameter part 38a
and four actions W41a to 4 by the through vane 40.
1d is formed, and the volumes of these working chambers change as the rotor 38 rotates, so that each working chamber has suction,
Performs compression and discharge actions (strokes). In FIG. 5a, working chambers 418 and 41d are in the early and late stages of the suction stroke, respectively, working chamber t1c is in the compression stroke, and working chamber 41d is in the discharge stroke. A discharge port 42 that opens into the action chamber of the discharge stroke is formed in the cylinder housing 34, and this discharge port 42 is connected to a discharge chamber 44 in the rear housing 36 via a discharge valve 43. The discharge port 10 is open.

Next, with reference to FIG. 4, a structure for connecting the low pressure refrigerant suction port 11 to the rear and front low pressure 9 medium suction ports 11a and 11b will be described. On the outer peripheral surface of the front end plate 32, there are holes 2 that reach these two intake ports 11a and 11b.
one horizontal hole 32b.

A distribution/valve mechanism 50 is airtightly attached to the side hole of the plate through a gasket 52, and a low pressure refrigerant suction boat 11 is connected to this mechanism 50. To explain in more detail, the distribution/valve mechanism 50 has a base plate 54, one side of the base plate 54 is integrally connected with the low pressure refrigerant suction port 11, and the other side of the base plate 54 has two
Main branch pipes 56, 58 are provided protrudingly. The aforementioned passages 11c and 11d are formed in these branch pipes 56 and 58, one end of which communicates with the inside of the low-pressure refrigerant port 11, and the other end connected to the side of the branch pipes 56 and 58.
The openings 1ie' and 11d' are provided. A check valve 60 made of a thin elastic metal plate or the like is disposed on the side surface of the branch pipe 56 where the opening 110' is provided, covering the opening 110', and its base end regulates the swing angle of the check valve 6o. It is held between the stopper 62 and the branch pipe 56. opening 11
A similar check valve and stopper are also attached to the side surface of the branch pipe 58 provided with d', but these are not shown. The horizontal holes 32b and 32C provided in the front end plate 32 are formed with dimensions and intervals to receive the branch pipes 56 and 58, respectively. Therefore, these horizontal holes 32b.

32C, and insert the branch pipe 5 into the side holes 32b and 32C through the hole in the gasket.
6.58, and tighten and fix the board 54 to the front end plate 32 with the screws 64, thereby connecting the distribution/valve mechanism 50 and the low pressure refrigerant suction port 11.
The passages 11c and 11d in the branch pipes 56 and 58 communicate with the low pressure refrigerant suction ports 11a and 11b when the check valve 60 is opened.

Next, the operation of the compressor 1 will be explained with reference to FIGS. 5a to 5d. In this case, the working chamber 41a sandwiched between the hatched through vanes will be described as soil.

When the rotor 38 rotates and the vane 40 on the leading side of the action chamber 41a comes to the position shown in FIG.
The suction force of the action chamber 41a is applied to the check valve 60 (FIG. 4) of the suction port 11a through the suction port 11a, and the low-pressure cold tofu begins to be sucked.

At this point, high-pressure refrigerant is flowing into the working chamber 41d on the front side of the first working chamber 41a from the high-pressure refrigerant suction port 12a.
Also, the effect t41d of the low pressure refrigerant suction port 11b on the front side
However, since the refrigerant pressure in this action chamber 41d is higher than the refrigerant pressure in the low-pressure refrigerant suction port 11, the check valve of the front low-pressure refrigerant suction port 11b is closed. is prevented from flowing out from the action chamber 41d to the low-pressure refrigerant suction port 11 side. Therefore, high-pressure refrigerant does not flow from the front working chamber 41d to the rear working chamber 41a.

Since the rotor 38 continues to rotate, the leading side vane 40 of the action 'J41a
Since the low-pressure refrigerant suction port 1111 on the front side opens into the action chamber 41a, the suction force of the action chamber 41a opens the check valve of the suction port 11b. Therefore, at this stage, the low-pressure refrigerant from the refrigerating/freezing evaporator 20 (FIG. 6) is sucked into the action chamber 41a from both the front and rear low-pressure refrigerant suction ports 11b and 11a. contains enough low-pressure refrigerant.

When the vane 40 on the leading side of the working ff 141a reaches the high-pressure refrigerant suction port 12a and opens this suction port 12a to the working chamber 41a (FIG. 5b), the cooling armor generator 18
Due to the pressure difference between the high-pressure refrigerant and the low-pressure refrigerant in the working chamber 41a, the high-pressure refrigerant flows into the working W41a from the suction port 12a and is mixed with the low-pressure refrigerant in the working chamber. And this action chamber 41
The refrigerant pressure in a is two low pressure refrigerant suction ports 11a and 11b.
When the pressure becomes higher than the closing pressure of the check valve t, the check valve t closes, and only high-pressure refrigerant flows from the suction port 12a to the action chamber 41.
flows into a.

The suction phase during which the low-pressure refrigerant is sucked into the working chamber is called the "early stage J of the suction stroke," and the suction phase during which the high-pressure refrigerant is sucked is called the "late stage J of the suction stroke.

The moment the vane 40 on the trailing side of the action 141a passes the tip of the high-pressure refrigerant suction port 12a (FIG. 5C), the flow of refrigerant into the action chamber 41a is stopped, and thereafter the action chamber 4
18 starts the compression stroke.

As the rotor 38 rotates, the volume of the action 141a gradually becomes smaller, and the action '! The refrigerant gas within 41a is gradually compressed and its pressure increases. When the vane on the leading side of the working chamber 41a reaches the discharge port 42 and opens the discharge port to the working chamber 41a, the compressed refrigerant gas is discharged from the discharge port 42.

As described above, after the low-pressure refrigerant from the refrigeration/refrigeration circuit 21 is sucked into the action chamber 41 of the compressor 1 and 1, the cooling circuit 1
After the high-pressure refrigerant from 7 is sucked into the same working chamber 41 and both refrigerants are mixed, the working chamber enters the compression stroke, and then the discharge stroke, and the refrigerant compressed in the compression stroke enters the working chamber 4.
1, enters the discharge port 44 via the discharge port 42 and the discharge valve 43, passes through the discharge port 10, enters the condenser 15, and is connected to the cooling circuit 17 as described below with reference to FIG.
and the suction boat i2. for high-pressure and low-pressure refrigerants of the compressor 1, which flow separately through the refrigeration circuit 21. The process of returning to step ii and being compressed again is repeated.

In the above embodiments, a through-vane type rotary compressor is used, but the present invention can also be applied to a rotasco type compressor.

[Brief explanation of the drawing]

Fig. 1 is a sectional view taken along line II in Fig. 2, Fig. 2 is an axial sectional view of the embodiment of the rotary vane type compressor of the present invention, No. 3N is a perspective view of the front end plate of the compressor, and No. 4 is a perspective view of the front end plate of the compressor. The figure is an enlarged perspective view showing details of the distribution/valve mechanism, Figures 5a to 5d are explanatory diagrams showing each operating stage of the compressor, and Figure 6 is a refrigeration cycle diagram. 1...Compressor, 10...Discharge port, 11...Low pressure refrigerant suction boat, 12...
・High pressure refrigerant suction port, 17... Cooling circuit, 21... Refrigeration freezing circuit, 11a... Low pressure refrigerant suction port on the return side, 11b...
...Front and rear low-pressure refrigerant inlets, 12a...Intake for high-pressure refrigerant, 32...Front end plate, 32b, 32c...Horizontal hole, 34... ...Cylinder housing, 38...
・〇-ta, 40... Vane, 42... Discharge port, 43... Discharge valve, 50... Distribution and valve mechanism, 56.58. ... Branch pipe, 60 ... Check valve.

Claims (1)

[Claims] a main body having a cylinder bore having a suction port for low-pressure refrigerant and a suction port for high-pressure refrigerant; a rotor rotatably mounted in the main body; and a rotor slidably mounted in a vane groove of the rotor. and a vane that cooperates with a main body and a rotor to form an action chamber, and as the vane rotates due to rotation of the rotor, the suction port for the low-pressure refrigerant first opens into the action chamber in the suction stroke. Thereafter, in a rotary vane compressor in which the high-pressure refrigerant suction port is configured to open into the working chamber, the low-pressure refrigerant suction port is divided into two parts and the two parts are separated by rotation of the vane. 1. A rotary vane compressor characterized in that the compressors are arranged side by side in the direction of the rotary vane compressor, and check valves are provided at each of the separate suction ports for low-pressure refrigerant.