CN118030532A - Horizontal compressor - Google Patents

Abstract

A horizontal compressor (100) can provide stable oil supply to a sliding member even when jolting occurs during movement, and reduce the oil filling amount. Comprising the following steps: a first housing (1) that houses the motor (2); a second housing (4) that houses the pump body (5); an intermediate partition plate (3) disposed between the first and second cases and having a through hole (311) formed at a substantially center thereof, the pump body comprising: a crankshaft (50) extending from a low-pressure chamber to a high-pressure chamber, a main bearing (51), cylinders (52, 55), and a sub-bearing (57) arranged in this order from a middle partition plate along the axial direction of the crankshaft, a journal portion of the main bearing is interposed between a through hole and the crankshaft, the space between the inner peripheral surface of the through hole and the outer peripheral surface of the journal portion is sealed, oil is stored in the bottom of the high-pressure chamber, an oil suction hole (571) is formed in the pump body, and an annular groove (512B) and an axial spiral groove (512A) communicating with the oil suction hole are formed in the inner peripheral surface of the main bearing.

Description

Horizontal compressor

Technical Field

The present invention relates to a horizontal compressor.

Background

Currently, a rotor compressor having a motor and a pump accommodated in one chamber is mostly applied to the household field, and thus is required to be generally operated in a stationary state and to be placed in a vertical state. In such a compressor, oil supply to sliding members such as bearings, cylinders, and crankshafts in a pump body is generally ensured by centrifugal force during operation. However, when the rotor compressor is applied to the functional moving field of high-speed rail and household sedans, oil in the cavity can be greatly oscillated when jolting occurs in the moving process because the oil in the rotor compressor is stored in the cavity, and the oil level is greatly changed.

In the case where, for example, oil in the cavity flows toward the side opposite to the oil suction hole, the oil level at the oil suction hole side may drop below the oil suction hole, and thus, it is difficult for the oil suction hole to suck oil, thereby making it difficult to supply stable and continuous oil supply to the sliding member, resulting in problems of large fluctuation in performance, insufficient reliability, and the like of the compressor.

Further, in order to avoid the above-mentioned case where the oil suction hole is difficult to suck the oil, it is necessary to charge a large amount of oil into the cavity in advance, resulting in an increase in the oil charge amount.

Disclosure of Invention

The present invention has been made in view of the above-described problems, and an object thereof is to provide a horizontal compressor that can provide a stable oil supply to a sliding member even if a large bump occurs during movement, and can reduce the oil charge amount.

In order to achieve the above object, a first aspect of the present invention provides a horizontal compressor comprising: a first housing that houses the motor and that is formed with an air inlet; and a second housing that houses the pump body, the second housing further including an intermediate partition plate disposed between the first housing and the second housing, the intermediate partition plate forming a low-pressure chamber with the first housing and a high-pressure chamber with the second housing, a through hole being formed at a substantially center of the intermediate partition plate, the pump body including: the low-pressure chamber is provided with a through hole, a crankshaft extending from the through hole to the high-pressure chamber, a main bearing, a cylinder and a sub-bearing which are sequentially arranged along the axial direction of the crankshaft from the middle partition plate, a shaft neck part of the main bearing is clamped between the through hole and the crankshaft, the inner peripheral surface of the through hole and the outer peripheral surface of the shaft neck part are sealed, oil is stored at the bottom of the high-pressure chamber, an oil suction hole for sucking the oil is formed in the pump main body, and an annular groove and an axial spiral groove which are communicated with the oil suction hole are formed in the inner peripheral surface of the main bearing.

According to the above-described structure, since the intermediate partition plate divides the chamber formed by the first casing and the second casing into the low-pressure chamber and the high-pressure chamber, and the oil suction hole is formed in the high-pressure chamber, when the horizontal compressor jolts substantially, since the high-pressure chamber is smaller than one chamber space in the past, the oscillation range of the oil in the high-pressure chamber becomes smaller, the oil level variation width becomes smaller, and the possibility that the oil suction hole is exposed from the oil level becomes smaller. Thereby, the possibility of sucking the oil to the oil suction hole can be improved. Further, an annular groove communicating with the oil suction hole is formed in the inner circumferential surface of the main bearing, the annular groove coating the oil sucked up from the oil suction hole on the outer surface of the crankshaft, and an axial helical groove temporarily storing and conveying the oil sucked up from the oil suction hole in the axial direction of the crankshaft. Therefore, the axial spiral groove can make the oil rotating with the rotation of the crankshaft more easily enter the groove than the linear groove, and the flow rate of the oil inside the spiral groove becomes smaller than the linear groove, so that the oil is less likely to leak from the spiral groove into the low-pressure chamber.

A horizontal compressor according to a second aspect of the present invention is the horizontal compressor according to the first aspect of the present invention, wherein a tip end of the axial spiral groove is provided in a shape not reaching a tip end surface of a journal portion of the main bearing.

According to the above configuration, since the tip end of the axial spiral groove is provided in a shape not reaching the tip end face of the journal portion of the main bearing, oil in the axial spiral groove can be prevented from leaking from the tip end face of the journal portion of the main bearing to the low pressure chamber. Thus, the amount of oil leakage from the high-pressure chamber to the low-pressure chamber can be reduced.

A horizontal compressor according to a third aspect of the present invention is the horizontal compressor according to the second aspect of the present invention, wherein a fluid return hole for communicating the low pressure chamber with the cylinder is formed in the intermediate partition plate.

According to the above configuration, since the fluid return hole communicates the low pressure chamber with the cylinder, it is possible to ensure that the gas sucked from the suction port of the low pressure chamber flows into the high pressure chamber through the fluid return hole. In addition, the oil accumulated in the bottom of the low-pressure chamber can flow back into the high-pressure chamber through the fluid return hole.

A horizontal compressor according to a fourth aspect of the present invention is the horizontal compressor according to the first aspect of the present invention, wherein a seal groove is formed in an inner peripheral surface of the through hole, and a seal is provided in the seal groove.

According to the above configuration, the seal groove is formed in the inner peripheral surface of the through hole, and the seal is provided in the seal groove, so that the space between the inner peripheral surface of the through hole and the outer peripheral surface of the journal portion is sealed by the seal. This can prevent the refrigerant in the high-pressure chamber from leaking into the low-pressure chamber through the gap between the inner peripheral surface of the through hole and the journal portion of the main bearing, and thus can avoid a decrease in energy efficiency.

A horizontal compressor according to a fifth aspect of the present invention is the compressor according to any one of the first to fourth aspects of the present invention, wherein the intermediate partition plate is of a split structure.

According to the above structure, since the intermediate partition plate is of a split structure, it is possible to easily mount the intermediate partition plate on the rotating shaft after mounting the motor, and the operation is simplified.

A horizontal compressor according to a sixth aspect of the present invention is the compressor according to the first or second aspect of the present invention, wherein the number of the cylinders is two.

According to the above configuration, the number of the cylinders is two, so that the gas in the high-pressure chamber can be sufficiently compressed to form a high pressure.

A horizontal compressor according to a seventh aspect of the present invention is the compressor according to the first or second aspect of the present invention, wherein the cylinder is one.

According to the above structure, the structure of the horizontal compressor can be simplified by arranging one cylinder.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following description will simply refer to the drawings used in the embodiments or the prior art. It is apparent that the drawings in the following description are only some embodiments of the present invention, and that other drawings may be obtained from these drawings without inventive effort for a person of ordinary skill in the art.

Fig. 1 is a cross-sectional view showing a schematic configuration of a horizontal compressor according to embodiment 1 of the present invention.

Fig. 2 is a schematic view showing a state in which an oil supply unit of a horizontal compressor according to embodiment 1 of the present invention is attached to a main bearing.

Fig. 3 is a schematic diagram showing an oil supply path in the horizontal compressor according to embodiment 1 of the present invention.

Fig. 4 is a schematic view showing an axial spiral groove and an annular groove in an inner peripheral surface of a main bearing in a horizontal compressor according to embodiment 1 of the present invention.

Fig. 5 is a schematic view showing the structure of an intermediate partition plate in a horizontal compressor according to embodiment 1 of the present invention

Fig. 6 is a schematic view showing the structure of an intermediate partition plate in the horizontal compressor according to embodiment 2 of the present invention.

Fig. 7 is a cross-sectional view showing the structure of a main bearing in a horizontal compressor according to modification 1 of embodiments 1 and 2 of the present invention.

Fig. 8 is a cross-sectional view showing the structure of a horizontal compressor according to modification 2 of embodiments 1 and 2 of the present invention.

(Symbol description)

100 Horizontal compressor

1 First shell

11 Suction port

10 Low pressure Chamber

2 Motor

21 Stator

22 Rotor

3 Middle partition board

31 Main body portion

311 Through hole

312 Seal groove

313 Seal

314. 314A fluid return orifice

32 Reinforcing part

4 Second shell

40 High pressure chamber

41 Exhaust port

5 Pump body

50 Crankshaft

51. 51' Main bearing

511. 511' Main body

511A, 511A' oil suction holes

511A1, 511A1' large diameter portion

511A2, 511A2' small diameter portion

512. 512' Journal portion

512A, 512A' axial helical groove

512B, 512B' annular groove

52 First cylinder

53 First piston

54 Cylinder partition

55 Second cylinder

56 Second piston

57 Auxiliary bearing

6 Oil supply assembly

61 Oil supply pipe

62 Oil suction port

7 Oil pool

L1 first oil passage

L2 second oil passage

Detailed Description

Hereinafter, various embodiments of the horizontal compressor according to the present invention will be described with reference to the accompanying drawings. The horizontal compressor of the present invention can provide stable oil supply to the sliding member even during the moving process and can reduce the oil filling amount. Fig. 1 is a cross-sectional view showing a schematic configuration of a horizontal compressor according to embodiment 1 of the present invention. Fig. 2 is a schematic view showing a state in which an oil supply unit of a horizontal compressor according to embodiment 1 of the present invention is attached to a main bearing. Fig. 3 is a schematic diagram showing an oil supply path in the horizontal compressor according to embodiment 1 of the present invention. Fig. 4 is a schematic view showing an axial spiral groove and an annular groove in an inner peripheral surface of a main bearing in a horizontal compressor according to embodiment 1 of the present invention. Fig. 5 is a schematic view showing the structure of an intermediate partition plate in the horizontal compressor according to embodiment 1 of the present invention. Fig. 6 is a schematic view showing the structure of an intermediate partition plate in the horizontal compressor according to embodiment 2 of the present invention. Fig. 7 is a cross-sectional view showing the structure of a main bearing in a horizontal compressor according to modification 1 of embodiments 1 and 2 of the present invention. Fig. 8 is a cross-sectional view showing the structure of a horizontal compressor according to modification 2 of embodiments 1 and 2 of the present invention.

Hereinafter, in each embodiment, the upper side, the lower side, the left side, and the right side of the first casing 1 and the second casing 4 in fig. 1 are respectively set to the upper side, the lower side, the left side, and the right side.

(Embodiment 1)

(Integral Structure of horizontal compressor 1)

Hereinafter, the general structure of the horizontal compressor 1 according to embodiment 1 of the present invention will be specifically described with reference to fig. 1 to 5.

As shown in fig. 1, in the present embodiment, a horizontal compressor 100 includes: a first casing 1, wherein the first casing 1 is positioned at the left side of the horizontal compressor 100, and an air inlet 11 is formed at the upper side; a second casing 4, wherein the second casing 4 is positioned at the right side of the horizontal compressor 100, and a discharge port 41 is formed at the upper side; and the middle partition plate 3 is positioned between the first shell 1 and the second shell 4, and forms a low-pressure cavity 10 with the first shell 1, forms a high-pressure cavity 40 with the second shell 4, and the pressure inside the high-pressure cavity 40 is larger than the pressure inside the low-pressure cavity 10.

In this way, the chamber surrounded by the first casing 1 and the second casing 2 is partitioned into the low pressure chamber 10 of low pressure and the high pressure chamber 40 of relatively high pressure by the intermediate partition plate 3, and even when the horizontal compressor 1 is subjected to horizontal reply jolting, since the chamber is partitioned into the two chambers of the low pressure chamber and the high pressure chamber, the high pressure chamber space provided with the oil suction hole becomes small, the oscillation amplitude of the oil in the space becomes correspondingly small, and the oil level becomes more stable. Thus, the stability of the oil supply can be ensured. In this way, the oscillation amplitude of the oil in the high-pressure chamber becomes small, and therefore the possibility that the oil suction hole is exposed from the oil surface becomes small. Therefore, the height requirement of the oil surface can be met by reducing the filling amount of the frozen oil. Thus, the filling amount of oil into the high-pressure chamber is reduced as much as possible as compared with the structure of one chamber.

Further, a motor 2 is housed in the low pressure chamber 10, and the motor 2 includes: a stator 21, wherein the stator 21 is arranged on the inner periphery side of the first shell 1; and a rotor 22, wherein the rotor 22 is coaxially provided on the inner peripheral side of the stator 21 with the stator 21.

A pump body 5 is housed in the high-pressure chamber 40, and the pump body 5 includes: a main bearing 51, the main bearing 51 including a main body portion 511 and a journal portion 512; a first cylinder 52, the first cylinder 52 being located on the right side of the main bearing 51 and being coaxially provided with a first piston 53 on the inner peripheral side; a second cylinder 55, the second cylinder 55 being located on the right side of the first cylinder 52 and being coaxially provided with a second piston 56 on the inner circumferential side; a cylinder partition 54, the cylinder partition 54 being disposed between the first cylinder 52 and the second cylinder 55; and a sub-bearing 57, the sub-bearing 57 being located on the right side of the second cylinder 55. The crankshaft 50 extends from the low-pressure chamber 10 through the intermediate diaphragm 3 and into the high-pressure chamber 40.

As shown in fig. 1 and 5, the intermediate partition plate 3 includes: a body portion 31 having a substantially disk-like shape, a through hole 311 being formed at a substantially center thereof, a seal groove 312 being formed on an inner peripheral surface of the through hole 311 so as to be recessed radially outward, and a seal 313 being accommodated in the seal groove 312; and a reinforcing portion 32, the reinforcing portion 32 extending from the main body portion 31 to the right into the high-pressure chamber 40. By providing the seal 313 between the through-hole 311 and the crankshaft 50, it is possible to avoid the refrigerant in the high-pressure chamber from leaking into the low-pressure chamber, resulting in a reduction in energy efficiency. The reinforcing portion 32 is formed in a shape capable of wrapping and fastening the outer peripheral wall of the journal portion 512 of the main bearing 51. In this way, the reinforcing portion 32 can secure the position of the main bearing 51 in the axial direction and the radial direction. In addition to the through-holes 311 of the main body 31, through-holes (not shown) are formed in the first cylinder 52, the cylinder partition 54, the second cylinder 55, and the sub-bearing 57, respectively. In this way, by providing the crankshaft 50 so as to penetrate the rotor 22 of the motor 2, the intermediate partition plate 3, the main bearing 51 of the pump body 5, the first cylinder 52, the cylinder partition plate 54, the second cylinder 55, and the sub-bearing 57 in this order, when the motor 2 rotates, the rotation is transmitted to the pump body 5 via the crankshaft 50, thereby driving the pump body 5 to compress the gas into high-pressure gas.

(Oil supply passage in Pump body)

In the present embodiment, as shown in fig. 2, the oil supply assembly 6 is inserted into the oil suction hole 511A of the main bearing 51, sucks oil from the oil pool 7 through the oil suction port 62, and supplies the oil between the inner peripheral surface of the main bearing 51 and the outer peripheral surface of the crankshaft 50 via the oil supply pipe 61. At this time, the oil suction hole 511A has a trapezoid shape, and includes a large diameter portion 511A1 for receiving the oil feed pipe 61 of the oil feed unit 6 and a small diameter portion 511A2 extending from the oil feed pipe 61 to the outer peripheral surface of the crankshaft 50. In this way, the oil from the oil feed pipe 6 of the oil feed unit 6 can be smoothly supplied to the outer peripheral surface of the crankshaft 50 via the small diameter portion 511A2.

Next, the oil transferred to the outer peripheral surface of the crankshaft 50 via the oil suction hole 511A flows along the first oil passage L1 in the axial direction of the crankshaft 50 and the second oil passage L2 around the circumferential direction of the crankshaft 50, respectively, as shown in fig. 3.

Here, the first oil passage L1 is formed to include an axial spiral groove 512A (see fig. 4) formed in the inner peripheral surface of the main body portion 511 of the main bearing 51 and an annular groove 512B (see fig. 4) formed in the inner peripheral surface of the main body portion 511 of the main bearing 51. Wherein the front end of the axial helical groove 512A extends to the front end face of the main bearing 51.

In this way, by forming the axial spiral groove 512A on the inner peripheral surface of the main bearing 51, the oil from the oil suction hole 511A can be more easily transferred to the axial spiral groove 512A in accordance with the rotation angle of the crankshaft 50 than the axial straight groove. Further, by forming the axial spiral groove 512A on the inner peripheral surface of the main bearing 51, the flow rate of oil in the groove can be reduced as compared with an axial straight groove, and the amount of oil leaking into the low pressure chamber through between the main bearing and the crankshaft can be avoided.

Further, by forming the annular groove 512B in the inner peripheral surface of the main bearing 51, the oil sucked up from the oil suction hole 511A can be temporarily stored and transferred between the main bearing 51 and the crankshaft 50 via the axial spiral groove 512A to lubricate both. Thereby, the performance of the main bearing can be ensured.

(Reflux of oil from Low pressure Chamber to high pressure Chamber)

Since when the horizontal compressor 1 is operated, oil in the high pressure chamber 40 may leak into the low pressure chamber 10 in the following three cases when the pump body 5 in the high pressure chamber 40 is operated. ① Oil between the crankshaft 50 and the sub-bearing 57, the first cylinder 52, the second cylinder 55, and the main bearing 51 in the high-pressure chamber 40 may leak into the low-pressure chamber 10 through a spiral oil groove in the main bearing axial direction. ② Oil within the interior of the crankshaft 50 within the high pressure chamber 40 may flow through the crankshaft bore to the front end within the low pressure chamber 10 and down. ③ A small amount of oil may be carried in the refrigerant flowing into the low pressure chamber 10. The oil that enters the low pressure chamber 10 in the above three cases may drop to the bottom of the low pressure chamber 10 to form an oil pool.

In view of the above, the horizontal compressor 1 according to the present embodiment is further provided with a fluid return hole 314 in the intermediate partition plate 3 as shown in fig. 5, and the fluid return hole 314 functions as a return hole for returning the oil accumulated in the bottom of the low pressure chamber 10 to the high pressure chamber 40, in addition to the communication hole for communicating the low pressure chamber 10 with the high pressure chamber 40 as described above.

Specifically, a low pressure lower than the pressure in the low pressure chamber 10 is generated at the suction port of the pump body 5, the oil in the low pressure chamber 10 is sucked into the pump body 5 by the pressure difference between the low pressure chamber 10 and the suction port of the pump body 5, a part of the oil droplets compressed by the pressure in the pump body 5 together with the gas and changed into a liquid state fall back into the oil pool 7 of the high pressure chamber 40, and a part of the oil droplets are sucked into the compression chamber and then flow back into the oil pool 7 through the gap between the parts of the pump body 5. In this way, an efficient circulation of the compressor oil supply path is achieved, thereby ensuring a stable oil level of the oil sump 7 in the high pressure chamber 40.

(Embodiment 2)

In embodiment 1, the structure and technical effects of the horizontal compressor 1 in which the intermediate plate 3 is integrally formed are specifically described. Hereinafter, the horizontal compressor 1 of the present embodiment will be described with reference to fig. 6. The horizontal compressor 1 of the present embodiment is identical to embodiment 1 described above except that the intermediate partition plate 3A is of a split structure.

Specifically, as shown in fig. 6, the intermediate partition plate 3A includes a first partition plate 31A and a second partition plate 32A, and a fluid return hole 314A is formed in the lower portion of the first partition plate 31A, and the fluid return hole 314A functions as a return hole for returning oil at the bottom of the low pressure chamber 10 to the high pressure chamber 40, in addition to the communication hole for allowing the low pressure chamber 10 to communicate with the high pressure chamber 40, as in the fluid return hole 314 of the above embodiment 1.

In this way, compared with the intermediate partition plate 3 of the integral structure, the intermediate partition plate of the present embodiment can obtain the technical effect of being easy to assemble and capable of being mounted on the rotating shaft after the motor is mounted.

Modification 1

In embodiments 1 and 2 described above, the tip of the axial spiral groove 512A formed in the inner peripheral surface of the main bearing extends as shown in fig. 4 up to the tip of the inner peripheral surface of the main bearing (i.e., to the left in fig. 4), but the present invention is not limited thereto, and the axial spiral groove 512A may be formed in a shape in which the tip shown in fig. 7 is closed and does not reach the tip surface of the journal portion 512'.

Specifically, as shown in fig. 7, the main bearing 51' includes a substantially disk-shaped main body portion 511' and a journal portion 512' extending leftward from the main body portion 511', and an oil suction hole 511A ' into which the oil feed unit 6 is inserted is formed in a lower portion of the main body portion 511', and the oil suction hole 511A ' includes a large diameter portion 511A1' into which the oil feed pipe 61 is inserted and a trapezoid formed as a straight hole radially inward (upper side in the drawing) from the large diameter portion 511A1' and having a smaller diameter than the large diameter portion 511A1' at a small diameter portion 511A2 '. An annular groove 512B 'and an axial spiral groove 512A' communicating with the small diameter portion 511A2 'are formed in the inner peripheral surface of the main bearing 51'.

In this way, since the tip end of the axial spiral groove does not reach the tip end surface of the journal portion, oil does not flow to the contact area (see fig. 7, end circle mark) between the tip end surface of the journal portion 512' and the crankshaft 50, and thus oil leakage from the contact area to the low pressure chamber can be avoided.

Modification 2

In embodiments 1 and 2, two cylinders are provided in each of the high-pressure chambers of the horizontal compressor, but the present invention is not limited to this, and one cylinder may be provided.

Hereinafter, a structure 100A of the horizontal compressor according to the present modification will be described with reference to fig. 8. The horizontal compressor 100A of the present modification is similar to the above-described embodiments 1 and 2, except that the second casing 4 includes one cylinder (i.e., the first cylinder 52A and the first piston 53A inside thereof).

Specifically, as shown in fig. 8, in the horizontal compressor 100A of the present modification, a main bearing 51 is inserted into the high-pressure chamber 40 formed by the intermediate partition plate 3 and the second casing 4, a first cylinder 52A is provided on the right side of the main bearing 51, a first piston 53A is provided in the first cylinder 52A, a sub-bearing 57 is provided on the right side of the first cylinder 52A, and through holes through which the crankshaft 50 passes are formed in the main bearing 51, the first cylinder 52A, and the sub-bearing 57.

As described above, according to the horizontal compressor of the present modification, the same technical effects as those of embodiment 1 and embodiment 2 described above can be achieved, in which the axial spiral groove is provided as the temporary oil pool on the inner peripheral surface of the main bearing to ensure the stability of the oil supply. In addition, by reducing the number of cylinders to one as compared with embodiment 1 and embodiment 2 described above, the structure of the horizontal compressor can be simplified.

In the foregoing, for the purpose of making the objects, technical solutions and advantages of the embodiments of the present invention more clear, the technical solutions of the embodiments of the present invention are clearly and completely described with reference to the drawings in the embodiments of the present invention, and it is apparent that the described embodiments are some embodiments of the present invention, but not all embodiments of the embodiments. All other embodiments, based on the embodiments of the invention, which are apparent to those of ordinary skill in the art without undue burden are within the scope of the invention.

Embodiments 1 to 2 and modifications 1 and 2 of the present invention are described, but the embodiments of the present invention may be obtained by combining elements of the embodiments described above without departing from the gist of the present invention, in addition to the embodiments described in the embodiments described above.

In the above embodiments, only one fluid return hole is formed in the intermediate partition plate, but the present invention is not limited to this, and a plurality of fluid return holes may be formed.

In the above embodiments, the annular groove serving as the temporary oil pool is formed only in the inner peripheral surface of the main bearing, but the present invention is not limited thereto, and the annular groove may be formed only in the inner peripheral surface of the main bearing or the inner peripheral surface of the cylinder liner, or both the inner peripheral surface of the main bearing and the inner peripheral surface of the cylinder liner.

In the above embodiments, the pump body includes two cylinders, but is not limited thereto, and may include one or more cylinders.

In the above embodiments, only one intermediate partition plate is provided in the equipment main body of the horizontal compressor, but the present invention is not limited thereto, and a plurality of intermediate partition plates may be provided.

In embodiment 2, the fluid return hole is formed only in the first partition plate, but the fluid return hole is not limited to this, and may be formed in the second partition plate or may be plural.

In the above embodiments, the small diameter portion of the oil suction hole is formed as a straight hole, but may be formed as a tapered hole having a narrow upper portion and a wide lower portion.

Claims (7)

1. A horizontal compressor, comprising: a first housing that houses the motor and that is formed with an air inlet; and a second housing that houses the pump main body,

It is characterized in that the method comprises the steps of,

The device also comprises an intermediate baffle plate, the intermediate baffle plate is arranged between the first shell and the second shell, forms a low-pressure cavity with the first shell and forms a high-pressure cavity with the second shell,

A through hole is formed at a substantially center of the intermediate partition plate,

The pump body includes: a crankshaft extending from the low pressure chamber to the high pressure chamber through the through hole, and a main bearing, a cylinder, and a sub-bearing disposed in this order from the intermediate partition plate along an axial direction of the crankshaft,

A journal portion of the main bearing is interposed between the through hole and the crankshaft,

The inner peripheral surface of the through hole is sealed with the outer peripheral surface of the journal part,

Oil is stored at the bottom of the high pressure chamber,

The pump body is formed with an oil suction hole sucking the oil,

An annular groove and an axial spiral groove communicated with the oil suction hole are formed on the inner peripheral surface of the main bearing.

2. The horizontal compressor of claim 1, wherein,

The tip of the axial helical groove is provided in a shape not reaching the tip surface of the journal portion of the main bearing.

3. The horizontal compressor of claim 2, wherein,

A fluid return hole that communicates the low pressure chamber with the cylinder is formed in the intermediate partition plate.

4. The horizontal compressor of claim 1, wherein,

A seal groove is formed on the inner peripheral surface of the through hole,

A seal is disposed within the seal groove.

5. The horizontal compressor as set forth in any one of claims 1 to 4, wherein,

The middle partition plate is of a split structure.

6. The horizontal compressor as set forth in claim 1 or 2, wherein,

The number of the cylinders is two.

7. The horizontal compressor as set forth in claim 1 or 2, wherein,

The cylinder is one.