JPH04153594A - Rolling piston type compressor - Google Patents

Abstract

PURPOSE:To improve efficiency, suppress vibration and noise and permit the superlow speed operation by forming an intermediate pressure chamber in a sealed casing and arranging an intermediate pressure compressor body and a high pressure compressor body in the intermediate pressure chamber. CONSTITUTION:Accompanied with the drive of a driving means 3, the rolling pistons 5b and 6b of the compressor bodies 5 and 6 of a compression means 4 revolve, and the low pressure fluid flows into the compression chamber 5c of an intermediate pressure compressor body 5 through a suction passage 5d, and is compressed to an intermediate pressure and discharged into a sealed casing 2 from a fluid discharge port 8e. A portion of the discharged fluid intrudes into the rolling piston 6b, and other portion flows into a compression chamber 6c through a suction passage 6l, and is compressed to a high pressure and discharged outside. Accordingly, the pressure of the fluid which flows into the compression chamber 6c in the compression cycle and the pressure in the shaft hole 6d of the rolling piston 6b become equal, and the flow-out of the fluid from the edge surface of the rolling piston 6b is prevented. Further, since fluid is compressed in multistage form, the torque variation of the rolling pistons 5b and 6b is reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a rolling piston compressor, and in particular,
This invention relates to measures against torque fluctuations during driving and measures to prevent fluid leakage at the end face of a rolling piston.

(Prior Art) Generally, as one type of compressor installed in a refrigerator or the like, a rolling piston type compressor as shown in Japanese Patent Application Laid-Open No. 167095/1983 is known.

As shown in FIGS. 4 and 5, this compressor includes an electric motor (b) and an electric motor (
The compressor body (C) connected to the cylinder (d) is housed in the compressor body (C).
) A rolling piston (e) is eccentrically provided within the cylinder (d), and front and rear plates (f) and (g) are attached to both upper and lower end surfaces of the cylinder (d),
Further, the blade (h) is attached to the cylinder (d).
), and is configured in the shape of a fixed airfoil that is pressed against the outer circumferential surface of the rolling piston (e).

A shaft hole (i) is formed in the center of the rolling piston (e), and a crankshaft (j) extending from the electric motor (b) is inserted into the shaft hole (i). The cylinder (d) also has a fluid inlet (k).
A sealed casing (a) is formed in the inlet (k).
One end of a suction pipe (N) passing through is connected.

On the other hand, a fluid discharge port (m) is formed in the rear plate (g), and the discharge port (m) communicates with the internal space (A) of the casing (a) via a discharge valve (n). It has become. Further, the casing (a) is provided with a discharge pipe (0) whose one end opens into the internal space (A) of the casing (a) and whose other end extends toward a condenser (not shown).

When this compressor is driven, the refrigerant gas flows into the suction pipe (
After the refrigerant gas flows into the cylinder (d) from the suction port (k) through the suction port (k) and is compressed by the rotation of the rolling piston (e), the refrigerant gas flows into the cylinder (d) by opening the discharge valve (n).
m) into the internal space (A) of the casing (a). The high-pressure refrigerant gas in the internal space (A) is then sent to the discharge pipe (0).

(Problem to be solved by the invention) However, in such a compressor, when the compressor is driven, the internal space (B) of the shaft hole (i) is at a high pressure similar to the discharge pressure of the compressor. On the other hand, since the pressure in the compression chamber (C) communicating with the suction port (k) is low, the differential pressure between the high and low levels is large, and a seal with lubricating oil or the like prevents refrigerant gas from leaking from the end face of the rolling piston (e). (Fig. 5 Arrow D
) is difficult to completely prevent, leading to a decrease in compressor efficiency. In addition, in such a compressor, since the low pressure fluid is raised to high pressure as the discharge pressure of the compressor with one rotation of the rolling piston (e),
Not only were there problems such as large torque fluctuations during the compression stroke of the refrigerant gas, resulting in vibration and noise, but it was also considered impossible to operate at ultra-low speeds. Therefore, it is possible to install a balance weight in order to suppress the above-mentioned vibration.In this case, since the heavy balance weight is rotated, there is a problem that mechanical loss is large and leads to a decrease in compressor efficiency. be.

The present invention has been made in view of the above, and aims to suppress the leakage of refrigerant gas from the end face of the rolling piston as described above, and to reduce torque fluctuations in the compression stroke of the refrigerant gas.

(Means for Solving the Problems) In order to achieve the above object, the present invention has a compressor main body in multiple stages, and the inside of the closed casing is set at an intermediate pressure.

Specifically, as shown in FIG. 1, the measures taken by the invention according to claim (1) include a drive means (3) and a drive means (3) connected to the drive means (3) in a sealed casing (2). Compression means (4
), the compression means (4) comprises at least one intermediate pressure compressor body (5) and a high pressure compressor body (6), each compressor body (5), (6) , cylinder (5a).

Rolling piston (5b) in (6a), (6b
), and the rolling piston (5b),
A shaft hole (5e) formed in (6b).

(6d) is constructed by fitting the drive shaft (3b) of the drive means (3) into the cylinder (5a).

(6a) and rolling piston (5b), (6b
) are in contact with the plates (7), (8) and (9) across the upper and lower end surfaces of the cylinders (5a), (6g) and the outer peripheral surfaces of the rolling pistons (5b), (6b). A suction passage (5c), (6c) is formed between the compression chambers (5c), (6c), and fluid is sucked into the compression chambers (5c), (6c).
5d), (Ml) is connected, and the discharge port of the intermediate pressure compressor main body (5) is communicated with the suction port of the high pressure compressor main body (6) and opened into the sealed casing (2), An intermediate pressure chamber (2b) is provided within the hermetic casing (2).
The intermediate pressure compressor main body (5) and the high pressure compressor main body (6) are arranged in the intermediate pressure chamber (2b).

In the invention of claim (2), in the rolling piston compressor according to claim (1), the rolling piston (5b) of each compressor main body (5), (6),
(6b) was disposed so as to be eccentric to the axial center of the drive shaft (3b) or in a direction opposite to that of the drive shaft (3b).

(Function) With the above configuration, in the invention according to claim (1), as the drive means (3) is driven, the rolling pistons (5b ),
(6b) rotates, and low-pressure fluid flows into the compression chamber (5c) of the intermediate-pressure compressor main body (5) through the suction passage (5d), compressing this fluid to intermediate pressure. Thereafter, this intermediate pressure fluid is discharged into the closed casing (2) from the fluid discharge port (8e). Part of the fluid discharged into the sealed casing (2) enters the rolling piston (6b) of the high-pressure compressor main body (6), and the other part enters the suction passage (6).
g) and flows into the compression chamber (6C) of the high-pressure compressor main body (6), compresses this intermediate pressure fluid to a high pressure, and discharges it to the outside. Therefore, during the compression stroke in the high-pressure compressor main body (6), the fluid flowing into the compression chamber (6C) and the pressure in the shaft hole (6d) of the rolling piston (6b) are equal, and the rolling piston (6b) No fluid leaks from the end face. Furthermore, in order to compress the fluid in multiple stages, torque fluctuations in the rolling pistons (5b) and (6b) of each compressor body (5) and (6) are reduced.

Moreover, in the invention described in claim (2), each compressor main body (5), (6) mouth to ring piston (5b),
(6b), the dynamic balance during rotational driving is ensured, and vibration and noise accompanying the rotation of the rolling pistons (5b), (6b) of the respective compressor bodies (5), (6) can be reduced.

(Example) Next, an example of the present invention will be described with reference to the drawings.

As shown in FIG. 1, a rolling piston compressor (1) according to the present invention includes a driving means (3) and a compressor main body (4) as a compression means housed in a sealed casing (2). It is configured.

The drive means (3) consists of an electric motor (3a) and a crankshaft (3b) as a drive shaft.

The electric motor (3a) is disposed in the upper part of the sealed casing (2), and includes a stator (3c) fixed to the inner peripheral surface of the sealed casing (2), and a stator (3c) disposed in the center of the stator (3c). It consists of a rotor (3d) installed.

The crankshaft (3b) has its upper end connected to the rotor (3d).
), and its lower end extends downward and is connected to the compressor main body (4), and transmits the rotational driving force of the rotor (3d) to the compressor main body (4). It looks like this. Furthermore, lubricating oil (◯) is stored at the bottom of the sealed casing (2), and the lower end of the crankshaft (3b) is immersed in this lubricating oil (0). A centrifugal pump (not shown) is disposed near the lower end of the crankshaft (3b), and when the compressor (1) is driven, the centrifugal pump pumps lubricating oil (0) into the compressor body (4). It is supplied to various places.

The compressor main body (4) is a fixture type, and is provided below the electric motor (3a) with a sub compressor main body (5) as an intermediate pressure compressor main body and a main compressor main body (5) as a high pressure compressor main body. 6) are arranged vertically in parallel, and the compressor main body (4) divides the internal space of the hermetic casing (2) into an upper high pressure chamber (2a) and a lower intermediate pressure chamber (2b).
).

As shown in FIGS. 1 and 2, the sub-compressor main body (5) includes a rolling piston (5b) housed in a cylinder (5a) fixed to the inner peripheral surface of the sealed casing (2). At the same time, a front plate (7) is attached to the upper end surface of the cylinder (5a), while a middle plate (8) is attached to the lower end surface, and both plates (7), (8
), a compression chamber (5c) is formed between the inner peripheral surface of the cylinder (5a) and the outer peripheral surface of the rolling piston (5b). Further, a refrigerant suction passage (5d) that opens into the compression chamber (5c) is formed in the cylinder (5a), and the suction passage (5d) includes a suction pipe (10) extending from an accumulator (not shown). ) are connected. On the other hand, a shaft hole (5e) is formed in the center of the rolling piston (5b), and a cam (3e) integrally formed with the crankshaft (3b) is provided in the shaft hole (5e).
is fitted through a needle bearing (3f). Thereby, the rolling piston (5b) is provided eccentrically with respect to the cylinder (5a), and a part of the outer circumferential surface of the rolling piston (5b) is in contact with the inner circumferential surface of the cylinder (5a). . Further, a guide groove (5f) extending in the radial direction of the cylinder (5a) is formed in the cylinder (5a), and a blade (5g) is inserted into and retracted from the guide groove (5f). It is freely arranged. A flat sealing material (not shown) is interposed between the upper surface of the blade (5g) and the front plate (7) to prevent leakage of refrigerant gas. The tip of the blade (5g) is pressed against the outer circumferential surface of the rolling piston (5b) by the spring and the pressure of refrigerant gas to be described later, and the blade (5g) and the rolling piston (5b) move into the compression chamber. (5c)
is divided into a low pressure chamber (5h) and an intermediate pressure chamber (5i).

Further, a through hole (7a) is formed in the front plate (7) and extends in the vertical direction with a diameter substantially matching the shaft diameter of the crankshaft (3b), and the crankshaft (3b) is inserted into the through hole (7a). It is rotatably supported at the top of the Also,
The clearance between the inner peripheral surface of the through hole (7a) and the crankshaft (3b) is sealed by an oil seal, and the inner space (B
) communication is blocked.

Further, the middle plate (8) is provided with the crankshaft (3b).
) is formed with a through hole (8a) having a slightly larger diameter than the shaft diameter of the shaft. Further, the middle plate (8) is formed with an intermediate pressure gas passage (8b) penetrating from its upper end surface to its lower end surface. The upper opening (
8c) is formed to open into the compression chamber (5c). Then, a beam is placed near this upper opening (8c).
A closed valve (8d) is provided. This reed valve (8d)
is made of a thin plate such as spring steel, and one end is fixed to the inner wall of the intermediate pressure gas passage (8b), and the other end is fixed to the inner wall of the intermediate pressure gas passage (5b).
c) The upper opening (8c) is opened and closed depending on the pressure inside. Specifically, when the pressure in the compression chamber (5c) rises to an intermediate pressure of about 50% of the predetermined discharge pressure of the compressor, the reed valve (8d) opens and the pressure in the compression chamber (5c) increases.
) and the intermediate pressure gas passage (8b) are communicated with each other.

As shown in FIGS. 1 and 3, the main compressor main body (6) has substantially the same structure as the sub-compressor main body (5) described above, and has a rolling piston (6b) in the cylinder (6a).
), the middle plate (8) is attached to the upper end surface of the cylinder (6a), the rear plate (9) is attached to the lower end surface, and the outer peripheral surface of the rolling piston (6b) and the cylinder (6a) are connected. A compression chamber (6c) is formed between the inner peripheral surface and the inner peripheral surface. In addition, the above rolling piston (
In the shaft hole (6d) of 6b), a cam (3g) integrally formed with the crankshaft (3b) is fitted with a 21 dollar bearing (3h).
This rolling piston (6
b) and the rolling piston (5b) of the sub-compressor main body (5) are set to be eccentrically positioned relative to the axis of the crankshaft (3b) or in opposite directions.

Further, the rolling piston (6b) is provided so that a part of its outer circumferential surface is in contact with the inner circumferential surface of the cylinder (6a). As a result, each rolling piston (5b)
, (6b) The dynamic balance during rotation is maintained. Further, a blade (6f) is provided in the guide groove (6e) in the cylinder (6a) so as to be freely retractable, and the tip of the blade (6f) is pressed against the outer circumferential surface of the rolling piston (6b). Compression chamber (
6c) is divided into an intermediate pressure chamber (6g) and a high pressure chamber (6h). Further, the cylinder (6a) is formed with a communication passage (61) that communicates with the aforementioned intermediate pressure gas passage (8b). This communication path (61) has an upper opening (6j
) is formed to substantially match the lower opening (8e) of the intermediate pressure gas passage (8b), and is divided into two passages below it. One end of this divided passageway is a lower passageway (6) formed so as to open into the intermediate pressure chamber (2b) in the sealed casing (2).
k), and the other end has one end connected to the compression chamber (6
c) is a side passage (6g) formed so as to communicate with it. In other words, some of the refrigerant discharged from the sub-compressor body (5) passes through the communication path (61) into the intermediate pressure chamber (2b) in the hermetic casing (2), and some of the refrigerant flows into the main pressure chamber (2b). It is supplied to the compression chamber (6c) of the compressor main body (6).

Further, the crankshaft (3) is attached to the rear plate (9).
A through hole (9a) having a slightly larger diameter than the shaft diameter of b) and extending in the vertical direction is formed, and the lower part of the crankshaft (3b) is supported in this through hole (9a) via a bearing (9b). There is. A high pressure gas passage (9c) penetrating from the upper end surface to the lower end surface is formed in this rear plate (9). The upper opening (9d) of this high pressure gas passage (9c) is open facing the compression chamber (6c) of the main compressor body (6). A riet valve (9e) is disposed near the upper opening (9d). Konooriito valve (9e)
is disposed in the intermediate pressure gas passage (8b) described above, or has one end connected to the high pressure gas passage (9c), similar to the one-tooth valve (8d).
) It is fixed to the inner wall and opens and closes the upper opening (9d) depending on the pressure inside the compression chamber (6c) at the other end. Specifically, when the pressure in the compression chamber (6c) reaches a high pressure state corresponding to a predetermined discharge pressure of the compressor, this gate valve (6c) opens.
9e) is opened and the compression chamber (6c) and high pressure gas passage (9C
).

A lower muffler (11) is integrally formed under the rear plate (9). This lower muffler (
11), a muffler outer plate (11a) is disposed on the lower end surface of the rear plate (9), and both (9) and (l
la) It consists of a closed space formed between. In addition, the front plate (7), middle plate (8), rear plate (9) and each cylinder (5a), (6a
) is formed with a cylinder internal passage (12), and the lower end of this/ring internal passage (12) communicates with the lower muffler (11). On the other hand, the upper end of the cylinder internal passage (12) communicates with an upper muffler (13) integrally formed with the front bullet (7). This upper muffler (13) is connected to the front plate (7).
A muffler outer plate (13a) is disposed on the upper end surface, and a space is formed between the two (7) and (13a).
There is a gap of a predetermined size (dimension t in Figure 1) between the front plate (7) and the muffler outer plate (13a) at its upper end.
) is formed. Then, the sealed casing (2
) has a discharge pipe (14) connected to a condenser (not shown) on the top surface.
is connected.

Next, the operation of this rolling piston type compressor (1) will be explained.

First, when the electric motor (3a) is driven, this driving force is transmitted through the crankshaft (3b) to each compressor body (5),
(6) rolling piston (5b).

(6b) and the rolling piston (5b) (6
b) rotates within the cylinders (5a), (6a).

This allows the refrigerant gas to be transferred from the suction pipe (10) to the suction passage (5).
d) into the low pressure chamber (5h) of the sub-compressor main body (5), and as the rolling piston (5b) rotates, the refrigerant gas becomes either the low pressure chamber (5h) or the intermediate pressure chamber (51). When the refrigerant gas is compressed and reaches an intermediate pressure state of about 50% of the high pressure as the discharge pressure of the compressor, this pressure opens the reed valve (8d) and connects the intermediate pressure chamber (51) and the intermediate pressure gas passage ( 8b).Thereby, the refrigerant gas in the intermediate pressure state passes from the intermediate pressure chamber (5i) through the upper opening (8C) of the middle plate (8) to the intermediate pressure gas passage (8C).
b) Discharge. The intermediate pressure gas discharged into the intermediate pressure gas passage (8b) flows into the communication passage (61) and partially passes through the lower passage (6k) to the intermediate pressure chamber (2b) of the closed casing (2). Then, another part flows into the compression chamber (6C) of the main compressor body (6) through the side passage (6g). A clearance exists between the intermediate pressure chamber (2b) and the internal space (B-) of the shaft hole (6d) of the rolling piston (6b) between the rear plate (9) and the crankshaft (3b). As a result, the internal space (B-) of the shaft hole (6d) of the rolling piston (6b) has an intermediate pressure. On the other hand, the intermediate pressure gas that has flowed into the compression chamber (6C) is compressed by the rotation of the rolling piston (6b) of the main compressor body (6), and when it reaches a predetermined high pressure, the lid valve (9e) is opened by the pressure. death,
The high-pressure refrigerant scum is discharged into the lower muffler (11) through the high-pressure gas passage (9C). In the compression stroke in this main compressor main body (6), the compression chamber (6C
) is equal to the pressure in the internal space (B') of the shaft hole (6d) of the rolling piston (6b). Refrigerant does not leak into the intermediate pressure chamber (6g) through the end face of 6b).

Furthermore, the high-pressure refrigerant gas discharged to the lower muffler (11) passes through the cylinder internal passage (12) to the upper muffler (13).
) and is discharged into the high pressure chamber (2a) through the gap between the muffler outer plate (13a) and the front plate (7). This high-pressure refrigerant gas passes through the air gap of the drive means (3) located in the high-pressure chamber (2a) and flows into the discharge pipe (14) as discharge gas from the compressor. At this time, the high-pressure refrigerant gas removes heat emitted from the drive means (3) and has a cooling effect on the drive means (3).

In this way, in the compressor (1) of this example, the intermediate pressure chamber (2b) in the hermetic casing (2) is in an intermediate pressure state, and the suction pressure of the main compressor body (6) and the rolling piston (
By equalizing the pressure inside the shaft hole (6d) of the rolling piston (6b), leakage of refrigerant from the end face of the rolling piston (6b) can be prevented, and compressor efficiency can be improved. In addition, since the refrigerant gas is compressed in multiple stages (two stages in this example), torque fluctuations in the rotation of the rolling piston of each compressor body are reduced, and vibration and noise when the compressor is driven are suppressed. , ultra-low speed operation is also possible. Furthermore, each rolling piston (5b).

(6b) is set in an eccentric direction relative to the axis of the crankshaft (3b) or in the opposite direction, so dynamic balance is maintained, and this also suppresses the generation of vibration and noise. .

Although the compressor main body in this example is composed of two compressor main bodies, a sub and a main compressor main body, the present invention is not limited to this, and three or more compressor main bodies may be employed. In this case, the eccentric position of the rolling piston of each compressor main body with respect to the axis of the crankshaft is appropriately set so as to ensure dynamic balance during rotational driving.

(Effects of the Invention) As described above, according to the present invention, the following effects are exhibited.

In the invention according to claim (1), since the pressure in the shaft hole of the rolling piston is equal to the fluid flowing into the compression chamber during the compression stroke in the high-pressure compressor main body, leakage of fluid from the end surface of the rolling piston is prevented. The compressor efficiency can be improved. In addition, since it is a multi-stage compression system, torque fluctuations in the rolling piston rotation of each compressor body are reduced, which not only suppresses vibration and noise when the compressor is driven, but also enables ultra-low speed operation. .

Further, in the invention as set forth in claim (2), vibration and noise can be reduced by ensuring dynamic balance during rotational driving of the rolling piston of each compressor main body. Furthermore, since there is no need to provide a balance weight as in the past, mechanical loss is reduced and compressor efficiency is improved.

[Brief explanation of the drawing]

1 to 3 show an embodiment of the present invention, and FIG. 1 is a longitudinal sectional view showing the internal structure of a rolling piston compressor;
FIG. 2 is a cross-sectional view of the sub-compressor main body, and FIG. 3 is a cross-sectional view of the main compressor main body. 4 and 5 show a conventional example, in which FIG. 4 is a diagram equivalent to FIG. 1, and FIG. 5 is a diagram equivalent to FIG. 2. (1) Rolling piston compressor (2) Sealed casing (2a) High pressure chamber (3) Drive means (3b) Crankshaft (drive shaft) (4) Compressor body (Compression means) (5)...Sub compressor main body (intermediate pressure compressor main body) (6
)...Main compressor body (high pressure compressor body) (5a)
(6a)...Cylinder (5b,), (6
b)...Rolling piston (5c), (6c)...
・Compressor (5d)...Suction path (5e), (6d)・Shaft hole (6g)...Side passage (suction path) (7)...Front plate (8)...Middle plate ( 9) Rear plate (1) Rolling piston compressor (2) Sealed cane/g (2a) High pressure chamber (3)/Drive means (3b) Crack shaft (4) Compressor body (5)/Sub Compressor body (6) Main compressor body (5a), (6a) Cylinder (5b),
(6b) Rolling piste/(5c), (6
c) Compressor (5d)/Suction passage (5e), (6d)...Shaft hole (6g) Side passage (7)/Front plate (8)...Middle plate (9)/Rear plate C 10 − Diagram opening diagram diagram

Claims (2)

[Claims] (1) A drive means (3) and a compression means (4) connected to the drive means (3) are housed in the hermetic casing (2), and the compression means (4) has at least one intermediate pressure It consists of a compressor main body (5) and a high pressure compressor main body (6), and each compressor main body (5), (6) has a cylinder (5a), (6).
rolling pistons (5b), (6b) are housed in a), and the rolling pistons (5b), (6b)
The drive shaft (3b) of the drive means (3) is fitted into the shaft holes (5e), (6d) formed in the cylinders (5a), (6a) and the rolling piston ( 5b) and (6b), the plate (
7), (8), and (9) are brought into contact with each other and the cylinder (5a
), the inner peripheral surface of (6a) and the rolling piston (5b),
Compression chambers (5c), (6c) are formed between the outer peripheral surface of (6b), and suction passages (5d), (6l) for sucking fluid are connected to the compression chambers (5c), (6c). The discharge port of the intermediate pressure compressor main body (5) is communicated with the suction port of the high pressure compressor main body (6) and is opened in the closed casing (2), and the closed casing (2)
An intermediate pressure chamber (2b) is formed within the intermediate pressure chamber (2b).
b) A rolling piston type compressor, characterized in that the intermediate pressure compressor main body (5) and the high pressure compressor main body (6) are disposed within the compressor. (2) In the rolling piston compressor according to claim (1), the rolling pistons (5b) and (6b) of each compressor body (5) and (6) are arranged relative to the axis of the drive shaft (3b). A rolling piston compressor characterized by being arranged so that eccentric directions are opposite to each other.