KR100208220B1 - Compressor of airconditioner - Google Patents

Abstract

The present invention discloses an improved compressor for driving an air conditioner.

The compressor of the present invention is formed between a suction room, first and second discharge rooms communicating with two cylinders, and first and second discharge rooms, respectively, and the first and second cylinders communicating with each of the suction rooms and two cylinders, respectively. A crankcase having first and second high pressure and low pressure holes for bypassing the second unloading valve room and the refrigerant in the first and second discharge rooms to the suction room, respectively; A suction flow passage which is assembled to the crankcase forming part to block the unloading valve chamber from the outside, and communicates with the suction chamber, and the first and second discharge passages communicating with the first and second discharge chambers, respectively; A crankcase cover having a discharge passage communicating the first and second discharge passages; Semi-opening type first unloading to selectively open and close the first and second unloading valve rooms with the suction room by selectively communicating the first high pressure and low pressure holes with the second high pressure and low pressure holes respectively installed in the crankcase. It is composed of four cylinders having a valve and a second opening valve of a fully open type, so that the amount of refrigerant can be precisely controlled in four steps.

Description

Compressors for Air Conditioning

TECHNICAL FIELD The present invention relates to air conditioners, and more particularly, to a compressor for driving a large cooling cycle.

An air conditioner that cools a room using a cooling cycle liquefies a refrigerant gas compressed at a high pressure in a compressor in a condenser, and then vaporizes it in an evaporator through an expansion valve. An air conditioner that performs cooling by vaporization heat, and is widely used throughout society.

For example, even in automobiles, it is used for comfortable environment in summer. Passenger cars have a relatively small space to cool, and a small cooling system is enough, but a bus has a lot of space to cool down. Therefore, a large cooling system is adopted. As a result, a bus air conditioner also requires a large capacity compressor for driving the cooling cycle. A multi-cylinder compressor is generally used.

On the other hand, the air conditioner is equipped with a temperature control device for properly controlling the temperature of the room, the temperature control method is to turn on the clutch of the compressor based on the room temperature at the time according to the selected temperature of the temperature controller provided in the air conditioner The method of controlling the drive of a compressor by turning it ON / OFF is mainly used.

However, this method of temperature control is not easy to control the temperature and the pressure pulsation of the refrigerant is so severe that it not only lowers the durability of the refrigerant moving pipe, but also momentarily overloads the engine that drives the vehicle, thus driving performance and engine performance. It will adversely affect the durability of the.

Accordingly, in recent years, a compressor is always driven, and a driving method in which an air conditioner controls cooling performance according to a selected temperature by selectively driving some cylinders among a plurality of cylinders by appropriately adjusting the amount of refrigerant introduced thereto is introduced. .

1 to 6 schematically show an example of such a conventional compressor. This six-cylinder compressor is equipped with two unloading valves (40) for capacity control in a crankcase (10) to control the capacity of two cylinders (not shown), and two cylinders Capacity control is not performed.

To this end, as shown in FIG. 2, three discharge rooms 12 and 13 are formed in the crankcase 10 to cover two cylinders around one suction room 11. In addition, two suction rooms 16 and 17 and bypass rooms 15 and 18 each having two unloading valves 40 are formed between the discharge rooms 12, 13 and 14, respectively. do. In addition, as shown in FIG. 5, the suction passage 21 and the discharge chambers 12, 13, and 14, which communicate with the suction chamber 11 of the crankcase 10, are disposed on the inner surface of the crankcase cover 20. The discharge passages 22 communicating with each other are formed to be separated from each other. Meanwhile, between the crankcase 10 and the cover 20, as shown in FIG. 4, the rooms 11 to 18 of the crankcase 10 are divided into the suction passage 21 and the discharge passage 22 of the cover 20. The separator 30 is interposed therebetween. The separation plate 30 includes two suction holes 31 for communicating the suction chamber 11 of the crankcase 10 and the suction passage 21 of the cover 20, and three discharge chambers of the crankcase 10. (12) 13, 14, and first to third discharge holes 32 to 34 are formed to communicate the discharge passage 22 of the cover 20, respectively. In addition, in the installation position of the two unloading valves 40 of the crankcase 10, as shown in FIG. 3, the high pressure hole 19a communicating with the second discharge room 13 which covers two cylinders whose capacity is not controlled, and the suction room ( Low pressure holes 19b communicating with 11 are formed, respectively.

Accordingly, as shown in FIG. 6, the capacity of each cylinder is selectively controlled by the operation of the unloading valve 40. That is, when power is not applied to the coil 46 of the unloading valve 40, the plunger 47 is elastically biased downward by the spring 48, thereby bypassing the valve body 41. The pass passage 41b is closed. Accordingly, the discharge pressure of the two cylinders, which are not capacity controlled, flows into the operating flow path 41a of the valve body 41 through the second discharge room 13 and the high pressure hole 19a and acts on the piston 43. The piston 43 moves downward along the liner 42 to close the inlet hole 10a of the crankcase 10. Then, the compressor closes the suction chambers 16 and 17, which respectively cover four cylinders whose capacity is controlled by the two unloading valves 40, so that only one third of the total capacity is the second discharge hole of the separator 30. Output through (33).

When power is applied to the coil 46 of the unloading valve 40 in this state, the plunger 47 rises while compressing the spring 48 by the magnetic force thereof, thereby bypassing the passage 41b of the valve body 41. Will open. Then, the pressure of the two-cylinder, which is not in capacity control, is released to the suction room 11 through the bypass passage 41b and the low pressure hole 19b, whereby the piston 43 is liner by the restoring force of the compression spring 44. By returning to the top of 42, the inlet hole 10a of the crankcase 10 is opened. Therefore, since the refrigerant flows through all the cylinders of the compressor, the compressor outputs all of its capacity through the first to third discharge holes 32 to 34 of the separator 30. In this case, when only one of the two unloading valves 40 is operated, the compressor outputs only two-thirds of the full capacity. The remaining code 5 is a coil housing, and 42a is flow path holes of the liner 42.

However, such a conventional compressor not only has to form as many as eight rooms 11 to 18 in the crankcase 10 to control the amount of refrigerant through the two unloading valves 40, but also each room 11 to 18. In order to divide the cover into the discharge passage 22 and the suction passage 21 of the cover 20, a separate separation plate 30 must be provided between the crankcase 10 and the cover 20, the structure is very complicated and As well as the increase in manufacturing labor cost, there was a problem that the cost significantly increased. In addition, the six-cylinder compressor, but the capacity control is variable only in three stages, there was a problem that precise temperature control of the air conditioner was difficult.

SUMMARY OF THE INVENTION An object of the present invention is to provide a compressor for an air conditioner capable of reliably distinguishing a discharge flow path and a suction flow path without a separate separator in view of the above-described conventional problems.

Another object of the present invention is to provide a four-cylinder air conditioner compressor that can precisely control the amount of refrigerant with a very simple structure while employing two unloading valves.

In order to achieve the above objects, the compressor for an air conditioner according to the present invention is a four-cylinder compressor for an air conditioner that drives a cooling cycle, and includes one suction room and first and second discharge rooms communicating with two cylinders, respectively. And first and second unloading valve rooms formed between the first and second discharge rooms and communicating the suction chamber and two cylinders, respectively, and the refrigerant in the first and second discharge rooms communicate with each other. A crankcase having first high and low pressure holes and second high and low pressure holes respectively bypassing the room; It is assembled in the room forming part of the crankcase to block the two unloading valve rooms from the outside, and communicates with the suction room and the first and second discharge rooms, respectively, in communication with the suction room and connected to the suction line of the refrigerant. A crankcase cover having a first and a second discharge passage connected to the discharge pipe of the discharge passage, and a discharge passage for communicating the first and second discharge passages with each other; A half-opening-type first unloading valve installed on an outer surface of the crankcase to selectively open and close the first unloading valve room with the suction room by selectively communicating the first high pressure and low pressure holes; It is installed on the outer surface of the crankcase and selectively communicates with the second high pressure and low pressure hole to open and close the second unloading valve room and the suction room, characterized in that it is configured to include a second unloading valve of the fully open type .

According to one preferred feature of the present invention, an unloading valve is installed in the unloading valve room so as to communicate with the suction room through its inlet hole, and is movably coupled in the liner with a liner having a plurality of flow path holes on a main surface thereof. A piston which is elastically biased to the opening side of the inlet hole, a working flow path fixed to the crankcase and communicating with the high pressure hole to guide the refrigerant in the discharge room into the liner, and in communication with the working flow path, the refrigerant in the discharge room passes through the low pressure hole. A valve body each having a bypass flow path leading to the valve body, a housing mounted on the valve body and having a coil selectively applied to the valve body, and elastically biased to close the bypass flow path in the housing, and the coil being driven by a magnetic force. And a plunger for selectively opening the bypass flow passage.

As described above, the present invention can be configured in four cylinders, but the amount of refrigerant can be adjusted in four stages, so that the temperature of the air conditioner can be more precisely controlled than in the related art, and the suction flow path is not provided without a separate separator plate as in the related art. Since the discharge flow path can be clearly distinguished, the cooling efficiency, stability, and reliability of the air conditioner can be improved, and the structure is simplified and the cost can be greatly reduced.

1 is a side view showing a conventional compressor.

2 is a front view showing a conventional crankcase.

3 is a plan view taken along A of FIG. 2.

4 is a front view showing the guide plate of FIG.

5 is a rear view showing a conventional crankcase cover.

6 is a cross-sectional view showing a conventional unloading valve.

7 is a front view showing a compressor according to the present invention.

8 is a partial cutaway side view thereof.

9 is a front view showing a crankcase of the present invention.

10 is a plan view thereof.

11 is a rear view showing the crankcase cover of the present invention.

FIG. 12 is a sectional view taken along B-B of FIG.

13 is a cross-sectional view showing an unloading valve of the present invention.

FIG. 14 is a sectional view taken along the line C-C of FIG. 13. FIG.

15 is a cross-sectional view showing the operation of the present invention.

* Explanation of symbols for main parts of the drawings

50: crank case

51: suction room (of crankcase)

52, 53: 1st and 2nd discharge room (of crankcase)

54, 55: 1st and 2nd unloading valve room (of crankcase)

56, 57: 1st high pressure and low pressure hole 58, 59: 2nd high pressure and low pressure hole

60: crankcase cover 61: suction flow path (of cover)

62, 63: first and second discharge passages (of the cover)

65: discharge passage

70, 80: first and second unloading valve

72, 82: liner (of the first and second unloading valves)

72a, 82a: Euro hole (in liner)

71, 83: pistons (of the first and second unloading valves)

81: valve body (of the second unloading valve)

85: coil (of the second unloading valve)

86: plunger (of the second unloading valve)

92a: working oil (of valve body)

92b: bypass flow path (of valve body)

Such specific features and other advantages of the present invention will become more apparent from the following description of the preferred embodiments with reference to the accompanying drawings.

7 to 14, the air conditioner compressor according to the present invention is preferably composed of four V-cylinder, two first and second unloading valve (at a predetermined position on the upper surface of the crankcase 50) 70 and 80 are provided to control two cylinder capacities, respectively. In addition, a crankcase cover 60 is assembled at one end of the crankcase 50 to block the inside thereof from the outside.

One suction room 51 is formed in the upper part of the crankcase 50 as shown in FIG. 9, and the first and second discharges communicate with two cylinders around the suction room 51, respectively. Rooms 52 and 53 are formed. In addition, first and second unloading valve rooms 54 and 55 are formed between the first and second discharge rooms 52 and 53 to communicate the suction rooms 51 with the two cylinders, respectively.

The first discharge room 52 is selectively connected to the suction room 51 by the first high pressure and low pressure holes 56 and 57 communicating with each other selectively through the first unloading valve 70, The second discharge room 53 is selectively connected to the suction room 51 by the second high pressure and low pressure holes 58 and 59 communicating with each other selectively through the second unloading valve 80. That is, the first and second high pressure holes 56 and 58 communicate the first and second discharge chambers 52 and 53 with the upper surface of the crankcase 50, respectively, and the first and second low pressure holes. The 57 and 59 communicate the suction room 51 with the upper surface of the crankcase 50, respectively.

On the other hand, as shown in FIG. 11, the inner surface of the crankcase cover 60 is formed on one side so as to correspond to the suction flow path 61 communicating with the suction room 51 of the crankcase 50, the suction flow path ( The first and second discharge passages 62 and 63 communicating with the first and second discharge rooms 52 and 53 of the crankcase 50 are respectively formed around the periphery 61. Accordingly, a blocking portion 64 is formed between the first and second discharge passages 62 and 63 to block the two unloading valve rooms 54 and 55 of the crankcase 50 from each other. As shown in FIG. 12, a discharge passage 65 is formed in 64 for communicating the first and second discharge passages 62 and 63 with each other. The suction passage 61 of the crankcase cover 60 is connected to a suction pipe passage (not shown) of the refrigerant, and for example, the second discharge passage 63 of the two discharge passages 62 and 63 discharges the refrigerant. It is connected to the pipeline.

Meanwhile, as shown in FIG. 13, the first unloading valve 70 according to the present invention has a piston 73 at which the passage holes 72a of the liner 72 are normally opened at 1/2 and The semi-opening and closing type of opening and closing only, and the second unloading valve 80 is configured of the fully-opening type in which the piston 83 completely opens and closes all the flow path holes 82a of the liner 82. The first and second unloading valves 70 and 80 of the present invention have the same configuration and function as the overall opening and closing amount of the first and second unloading valves 70 and 80. For convenience of description, the second unloading valve 80 will be described as an example. Shall be.

In FIG. 14, the second unloading valve 80 is coaxially provided with a liner 82 communicating with the inlet hole 50a in the second unloading valve room 55 of the crankcase 50. A plurality of flow path holes 82a communicating with the second unloading valve room 55 of the crankcase 50 are formed at the main surface of the liner 82, preferably at a position biased toward the inlet hole 50a.

The outer surface of the crankcase 50 is provided with a valve body 81, which preferably consists of the upper and lower bodies 91, 92 are mutually coupled. On the outer surface of the lower body 92, a support bolt 93 positioned inside the liner 82 extends to an appropriate length, and the support bolt 93 is screwed with a cylindrical guide (89).

The lower body 92 communicates with the second discharge chamber 53 through the second high pressure hole 58 of the crankcase 50 to operate the hydraulic flow path 92a for guiding the high pressure refrigerant into the liner 82. The bypass passage 92b is formed in selective communication with the working passage 92a to guide the refrigerant in the second discharge chamber 53 to the suction chamber 51 through the second low pressure hole 59, and the upper body In the center of the 91, a slot 91a communicating with each of the flow paths 92a and 92b of the lower body 92 is formed.

In addition, on the upper body 91 of the valve body 81, a coil housing 85 having a coil 86 to which power is selectively applied is installed. In the center of the coil housing 85, an upper body 91 is provided. A plunger 87 for selectively opening and closing the bypass passage 92b through the slot 91a is movably installed and elastically biased to close the bypass passage 92b by the spring 88.

On the other hand, the piston 83 for opening and closing the flow path holes 82a is inserted in the liner 82 so as to be movable. An open upper end of the piston 83 is provided with a cover plate 90 for shielding the inside thereof, and a compression spring 84 is provided between the cover plate 90 and the flange 89a of the guide 89. The piston 83 is elastically biased toward the inlet hole 50a to be interposed to close the flow path holes 82a of the liner 82.

When the second unloading valve 80 is not supplied with power to the coil 86, the plunger 87 is elastically biased downward by the spring 88 so that the valve main body 81 passes the bypass flow path 92b. Will be closed. Accordingly, the discharge pressure of the cylinder acts on the piston 83 through the second high pressure hole 58 and the working flow path 92a to close the flow path holes 82a of the liner 82.

On the other hand, when power is applied to the coil 86, the plunger 87 rises while compressing the spring by the magnetic force, thereby opening the bypass passage 92b of the valve body 81. As a result, the discharge pressure of the cylinder exits the suction chamber 51 through the bypass passage 92b and the second low pressure hole 59, whereby the piston 83 is moved upward by the restoring force of the compression spring 84. By returning to, the flow path holes 82a of the liner 82 are opened.

An operation of the compressor for an air conditioner according to the present invention configured as described above will be described with reference to FIG. 15.

In FIG. 15, (a) is a state in which power is not applied to both unloading valves 70 and 80. In this case, since the first unloading valve 70 is half-opened, The refrigerant is sucked into the corresponding cylinders through the first unloading valve room 54. Accordingly, the discharge pressure acts on the piston 73 of the first unloading valve 70 through the first discharge chamber 52 and through the first high pressure and low pressure holes 56 and 57. The loading valve 70 is closed. At the same time, the discharge pressure of the first discharge room 52 flows into the second discharge room 53 through the discharge passage 65 of the crankcase cover 60, and then the second high pressure and low pressure holes 58 ( The second unloading valve 80 is also closed by acting on the piston 83 of the second unloading valve 80 through 59. Thus, the compressor will output only one quarter of its total capacity.

On the other hand (b) is the power is applied only to the first unloading valve 70, in this case the discharge pressure of the cylinder through the first high pressure and low pressure holes 56, 57 through the suction room 51 By bypassing the piston 73 of the first unloading valve 70 to completely open the flow path holes (72a) of the liner (72). At this time, since the second unloading valve 80 is completely closed, the compressor outputs only 1/2 of the total amount.

On the other hand (c) is a state in which power is not applied to the first unloading valve 70, the power is applied only to the second unloading valve (80). In this case, the first unloading valve 70 is closed and only the second unloading valve 80 is completely opened. Since the first unloading valve 70 of the present invention is a half-opening type, the corresponding cylinders are also half It will output in capacity. Accordingly, since the two cylinders corresponding to the second unloading valve 80 are output in a full amount, the compressor outputs only 3/4 of the total capacity.

On the other hand (d) is a state in which power is applied to both the first and second unloading valves 70, 80, in this case the piston 73 of the first and second unloading valves 70, 80 The 83s completely open the flow path holes 72a and 82a of the liner 72 and 82. Accordingly, all of the first and second unloading valve rooms 54 and 55 are in full communication with the suction room 51 so that all the cylinders perform compression. Thus, the compressor outputs at its total capacity.

As described above, according to the present invention, since the amount of refrigerant can be adjusted in four stages while being configured as a four-cylinder compressor, the temperature of the air conditioner can be adjusted to a more precise and comfortable optimum state while having a simple configuration as compared with the conventional art. . In addition, the suction flow path and the discharge flow path of the refrigerant can be reliably distinguished without providing a separate separator as in the prior art, and the structure of the compressor can be adjusted in four stages even if only five refrigerant rooms are formed in the crankcase. Can be much simplified compared to the prior art.

Therefore, the present invention has a very excellent effect that can reduce the cost of the cooling efficiency and stability and reliability of the air conditioner as well as the structure of the compressor is simplified.

Claims (2)

A four-cylinder compressor for an air conditioner that drives a cooling cycle, comprising: a suction chamber 51, first and second discharge chambers 52 and 53 communicating with two cylinders, respectively, and the first and second cylinders. First and second unloading valve rooms 54 and 55 formed between the discharge rooms 52 and 53 and communicating the suction chamber 51 with the two cylinders, respectively; and the first and second discharges. First high pressure and low pressure holes 56 and 57 and second high pressure and low pressure holes 58 and 59 which communicate with refrigerants in the rooms 52 and 53 to bypass the suction room 51, respectively. A crankcase 50 having a); The suction passage 61 is assembled to the room forming part of the crankcase 50 to block the two unloading valve rooms 54 and 55 from the outside, and communicates with the suction room 51 and is connected to the suction pipe path of the refrigerant. ), First and second discharge passages 62 and 63 in communication with the first and second discharge chambers 52 and 53, respectively, and connected to the discharge line of the refrigerant, and the first and second discharge passages 62 and 63. A crankcase cover 60 each having a discharge passage 65 for communicating the discharge passages 62 and 63 with each other; It is installed on the outer surface of the crankcase 50 to selectively communicate the first high pressure and low pressure holes (56, 57) to selectively open the first unloading valve room 54 with the suction room 51 A half-opening-type first unloading valve 70 which opens and closes; It is installed on the outer surface of the crankcase 50 and selectively communicates the second high pressure and low pressure holes 58, 59 to selectively connect the second unloading valve room 55 with the suction room 51. Compressor for air conditioning, characterized in that it comprises a second opening and closing valve (80) of the fully open type to open and close. The second unloading valve 80 is installed in the unloading valve room 55 to communicate with the suction room 51 through the inlet hole 50a, and has a plurality of flow paths on a main surface thereof. A liner 82 having a hole 82a, a piston 83 movably coupled in the liner 82 and elastically biased to an open side of the inlet hole 50a, and fixed to the crankcase 50; A working flow path 92a which communicates with the second high pressure hole 58 and guides the refrigerant in the second discharge room 53 into the liner 82, and communicates with the working flow path 92a to allow the second discharge room ( A valve body 81 having a bypass flow path 92b for guiding the refrigerant of 53) to the suction room 51 through the second low pressure hole 59, and installed on the valve body 81; The coil housing 85 having the coil 86 selectively applied therein and the bypass passage 92b in the coil housing 85 are closed. And a plunger (87) which is elastically biased and selectively opens the bypass flow path (92b) by the magnetic force of the coil (86).