JPH0123673B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION BACKGROUND OF THE INVENTION With the rapid miniaturization of hermetic motor compressor devices, many new problems have arisen that must be solved. The major problem caused by compact construction is noise generation. As expected, the exhaust noise increases in a compact structure, but the amount of noise on the intake side has also reached a noise level that must be reduced, especially considering noise reduction on the exhaust side.

Disclosure of the Invention In a multi-cylinder reciprocating airtight compressor,
The intake plenum for the two opposing cylinders is divided into two chambers by a partition. The partition has a pair of holes that allow partially restricted fluid access between the two chambers. Each chamber also communicates with a pair of inlets. As a result, each chamber can receive suction gas directly from its associated inlet, and can also receive suction gas from other chambers by means of fluid passing in turn through the inlet of the other chamber, the other chamber, and said holes. Inhalation gas can also be received from the chamber. Due to the different lengths of the flow paths and the restrictive effect of the holes, each chamber primarily supplies gas to its respective piston chamber. However, since each inlet communicates with both chambers, there is continuous flow in each inlet, rather than a periodic on-off flow dependent on piston motion. Although the flow through each inlet is continuous, the flow rate depends on which cylinder is on the suction stroke, and the gas flow is smooth.

The purpose of the present invention is to generate pulses (pulsations) due to suction pressure.
The objective is to optimally attenuate the

Another object of the invention is to reduce intake noise.

Yet another object of the invention is to connect each suction pipe to a plurality of piston chambers by passages of different lengths, and to connect each suction pipe to a plurality of piston chambers by passages of different lengths. and two suction pipes. The above objects and other objects that will become apparent from the following description are achieved by the present invention.

Basically, the piston chamber of the first cylinder communicates with the suction gas by two channels. The first flow path has a shorter distance to the first piston chamber than the second flow path, and in addition, the second flow path has a restriction in the flow path to the first piston chamber. ing. The piston chamber of the second cylinder communicates with the suction gas by two channels identical to the aforementioned channels. the first passage has a longer distance to the second piston chamber than the second passage;
It also includes a flow restriction in the flow path to the second piston chamber. This arrangement results in a plurality of cylinder-dependent suction gas flows in each passage, thereby creating a continuous flow in each suction passage.

Embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS In FIG. 1, a gas-tight motor compressor is shown at 10 extending into an outer shell formed by a lower portion 11 and an upper portion 12 welded together. Overall shown by. An electric motor 14 and a compressor 16 are arranged inside the outer shell.
The compressor 16 is arranged above the motor 14 so that its axis coincides with the axis of the motor 14.

Motor 14 includes a stator 15 and a rotor (not shown). The rotor is connected to and drives a crankshaft (not shown) supported within the cylinder block 20. Figures 2 to 4
In the figure, the cylinder block 20 receives an intake valve guide 40, and the cylinder block 20 also receives an intake valve guide 40.
0 receives the valve plate assembly 50.
Valve plate assembly 50 is received within inlet seal 60. A gasket 70 separates the cylinder head 80 from the seal 60. As best shown in FIG. 1, the cylinder block 20, valve guide 40, valve plate assembly 50, seal 60, and gasket 70
and cylinder head 80 are bolted together with bolts 90.

In FIG. 2, cylinder block 20 defines two piston chambers 21 and 22 surrounded by an intake plenum. The intake plenum is divided into two parts 23a and 2 by the partition wall 24.
It is divided into 3b. Partition wall 24 has two holes 24a and 24b formed to provide limited passage of fluid between the two portions 23a and 23b of the intake plenum.

The cylinder block is shown in detail in FIGS. 3-6, the figures being taken along several cross-sections for the purpose of continuously illustrating the flow paths. In FIG. 3, the two inlet seals define four inlet gas supply or inlet tubes 60a-60d. Tubes 60a and 60d communicate with plenum 23a, and tubes 60c and 60d communicate with plenum 23b. Holes 24a and 24b
provides restricted fluid access between plenums 23a and 23b. Inlet seals 60 and 61 are identical and surround valve plate assemblies 50 and 51, respectively, and are further separated from cylinder heads 80 and 81 by gaskets 70 and 71, respectively.

The tubes 60a-60d each communicate with the piston chamber 21 or 22 when the respective piston is on its intake stroke. That is, tubes 60a and 60b
sends gas to the intake plenum 23a, while the pipe 6
0c and 60d send gas to the intake plenum 23b. The intake plenums 23a and 23b communicate through the holes 24a and 24b of the partition wall 24, so the pipes 60a to 60d and the intake plenum 23a
This means that fluid continues to flow between the two parts and 23b. The flow is a unidirectional flow toward the intake plenum following the intake stroke of the piston.

Assuming that the piston in the piston chamber 21 is in the suction stroke and the piston in the piston chamber 22 is in the exhaust stroke, suction pressure is created in the intake plenum 23a. Coolant extending within the shell of the hermetic motor compressor unit 10 is then drawn into the tubes 60a and 60b and into the rectangular space 64 surrounding the valve plate assembly 50. The rectangular space 64 directly communicates with the intake plenum 23a. Coolant is drawn into the piston chamber 21 from the space 64 and the plenum 23a through the inlet hole 52. Intake plenum 23a
is in a relatively vacuum state compared to the intake plenum 23b, so the air flow from the intake plenum 23b to the hole 2
Further coolant flows into the intake plenum 23a through 4a and 24b. By this, next,
The plenum 23b is in a vacuum compared to the interior of the outer shell of the hermetic motor compressor device 10, and the coolant is drawn into the tubes 60c and 60d and flows into the plenum 23b through the rectangular space 65. The flow path from the tubes 60a and 60b to the piston chamber 21 is considerably shorter than the flow path from the tubes 60c and 60d to the piston chamber 21, and
4a and 24b;
Additionally, because each stroke takes less time, the fluid flow rate through tubes 60a and 60b is less than that of tubes 60c and 60.
This is considerably higher than the fluid flow rate passing through d. However, since the fluid always flows through each of the pipes 60a to 60d, there is no break in the flow, and as a result, there is no noise. Similarly, when the piston of the piston chamber 22 is on the suction stroke, the flow passing through the pipes 60c and 60d is higher than that of the pipes 60a and 60d.
This also applies when the flow is greater than that passing through b.

From the foregoing, it will be apparent that the flow of gas into each intake plenum is continuous even when the corresponding piston is on its exhaust stroke. However, the rate of gas flow in the two intake plenums and corresponding tubes varies depending on which piston is on the intake stroke.

Although the invention has been described in detail with respect to specific embodiments, other forms may occur to those skilled in the art. For example, one or both of the holes 24a and 24b in the partition wall can be replaced with a tube, thereby achieving even better noise reduction. Accordingly, the invention is limited only by the scope of the claims.

[Brief explanation of drawings]

FIG. 1 is a sectional view of a motor compressor device employing the present invention. FIG. 2 is an exploded view of the invention, partially shown in cross section. FIG. 3 is a cross-sectional view showing the fluid flow path. Figure 4 shows
FIG. 3 is a vertical cross-sectional view showing a fluid flow path. FIG. 5 is an end view of the crankcase. FIG. 6 is a cross-sectional view taken along the line - of FIG. DESCRIPTION OF SYMBOLS 10... Airtight motor compressor, 11... Lower part of outer shell, 12... Upper part of outer shell, 14... Electric motor, 15... Stator, 16... Compressor, 20... Cylinder block, 21... ...Piston chamber, 22...Piston chamber, 23
...Intake plenum, 24...Partition wall, 24
a, 24b... Hole in partition wall, 40... Intake valve guide, 50... Valve plate assembly, 51
... Valve plate assembly, 52 ... Inlet hole, 6
0... Intake port seal, 60a to 60d... Intake gas supply pipe, 61... Intake port seal, 64... Rectangular space (chamber), 65... Rectangular space (chamber), 70... Gasket, 71 ...Gasket, 80...Cylinder head, 81...Cylinder head, 90...Bolt.

Claims (1)

Claims: 1. An intake pulse damping device for a hermetic compressor, comprising a crankcase housing and restricted fluid communication means defining a plurality of intake plenums, each intake plenum defining a piston channel. said intake plenums have an intake air supply means for supplying suction gas, and further have fluid flow paths between each of said intake plenums. The restricted fluid communication means connects each of the intake plenums with each other to form a gas supply means, whereby the piston chamber is in communication with each of the intake air supply means to provide mutual fluid flow. an inspiratory pulse attenuation device which allows fluid to flow continuously within each of said inspiratory supply means at all times. 2. An intake pulse damping device for a two-cylinder hermetic compressor, which is connected to a crankcase housing defining two intake plenums and a first intake plenum of the intake plenums, and allows fluid to flow between them. a first piston chamber that is connected to a second one of the intake plenums and that is in fluid flow therewith; a first intake air supply means for supplying intake gas to the intake plenum, a second intake air supply means for supplying intake gas to the second intake plenum, the first piston chamber and the first piston chamber; a restricted fluid communication passage is formed between the second piston chamber and the first intake air supply means; and a restricted fluid communication passage is formed between the second piston chamber and the first intake air supply means. a restricted fluid communication connecting the first and second intake plenums to form a restricted fluid communication flow path between the first intake plenum and the second intake plenum; an inspiratory pulse damping device comprising: means;