WO2012117599A1

WO2012117599A1 - Multistage-compression rotary compressor and compression rotary compressor

Info

Publication number: WO2012117599A1
Application number: PCT/JP2011/071493
Authority: WO
Inventors: 山口　賢太郎; 桑原　修; 周平諫山
Original assignee: 三洋電機株式会社
Priority date: 2011-02-28
Filing date: 2011-09-21
Publication date: 2012-09-07
Also published as: CN103415705B; CN103415705A; JPWO2012117599A1

Abstract

[Problem] To provide a two-stage compression rotary compressor that can provide an inexpensive, highly efficient compression function, and that can also reduce installation space. [Solution] A multistage-compression rotary compressor is provided with first and second rotary compression elements (3, 4) via an intermediate partition plate (5), and the second rotary compression element (4) has an internal medium pressure structure configured from a roller (43) and a vane (44) in contact with the roller (43). Some coolant gas compressed into a high-pressure state by the second rotary compression element is fed into a spring chamber (412) within an upper cylinder (41). A bypass passage (45B) that applies some of the coolant gas with the vane (44) as a back pressure of the vane (44) is provided on the inside of an upper supporting member (45). In order to collect and return oil, which has been fed into a spring chamber (42) through the bypass passage (45B) with gas, to the inside of a sealed vessel (1A), a collection port (51A) opens when the vane (44) advances and a collection passage (51) that communicates with the space within the sealed vessel (1A) is provided inside the intermediate partition plate (5).

Description

Multistage compression rotary compressor and compression rotary compressor

The present invention relates to a rotary compressor that includes a drive element and a single or multiple-stage rotary compression element driven by the drive element in an airtight container, and compresses the refrigerant by the rotary compression element. The present invention relates to a compression-type rotary compressor having elements in multiple stages and a compression-type rotary compressor having a single rotary compression element.

Conventionally, various types of compression-type rotary compressors have been proposed and developed. One of them is a compression-type rotary compressor having multiple stages of rotary compression elements, for example, a two-stage type compression rotary compressor. A compressor is known (see, for example, Patent Document 1).

As shown in FIGS. 7 and 8, the rotary compressor 100 has an internal intermediate pressure structure, and refrigerant gas is sucked into the low pressure chamber side of the lower cylinder 102 from the suction port 103 of the first rotary compression element 101. The intermediate pressure is compressed by the operation of the roller 104 and the vane 105, and is discharged from the high pressure chamber side of the lower cylinder 102 to the discharge silencer chamber 130A through a discharge port (not shown).

In this way, the intermediate pressure is obtained, and is discharged from the high pressure chamber side of the lower cylinder 102 through the discharge port (not shown) and the muffler chamber 130A of the lower support member 130 into the sealed container of the rotary compressor 100. In other words, when the first stage compression operation is performed, the inside of the sealed container becomes an intermediate pressure. The intermediate-pressure refrigerant gas discharged into the sealed container is cooled by removing heat from the sealed container.

Then, the refrigerant gas in the intermediate pressure state passes through a suction passage (not shown) formed in the upper support member 140 from the suction port (not shown) of the upper cylinder 113 of the second rotary compression element 111 to the cylinder chamber 119. The air is sucked into the low pressure chamber, and the second stage compression operation is performed by the operation of the roller 114 and the vane 115. As a result, the refrigerant gas becomes a high pressure and high temperature state, passes through a discharge port (not shown) from the high pressure chamber side, passes through a discharge silencer chamber 140A formed in the upper support member 140, and is connected to the external pipe of the sealed container by a refrigerant discharge pipe (not shown). It is discharged into the (refrigerant circuit).

The

vanes

105 and 115 attached to the rotary compressor 100 are installed in grooves provided in the radial direction of the

cylinders

102 and 113, and are inserted movably in the radial direction of the

cylinders

102 and 113. ing. For example, in the

cylinders

102 and 113 shown in FIG. 8, a storage portion (hereinafter referred to as “spring”) that opens to the rear side (sealed container side) of the vane 105 and to the outside of the cylinder 102 (sealed container side). 107A) 107A is formed. The spring chamber 107A is inserted with a spring member 107 that constantly urges the vane 105 toward the roller 104, and then plugged into the plug 108 to prevent the spring member 107 from popping out. It is out. FIG. 8 shows the spring chamber 107A and the plug 108 of the lower cylinder 102, but the upper cylinder 113 has the same configuration.

Conventionally, in a two-stage compression rotary compressor having an internal intermediate pressure structure as described above, generally, oil necessary for sealing a high-pressure portion of a rotary compression element that is in a high-pressure state, which is the second stage, is combined with refrigerant gas. Oil is supplied directly to the high-pressure part in the sealed container. However, a part of the oil is often discharged together with the refrigerant gas to the refrigeration cycle outside the sealed container. In view of this, there has also been proposed a configuration in which oil discharged together with the refrigerant gas to the refrigeration cycle is collected immediately after being discharged from the sealed container of the rotary compressor (see, for example, Patent Document 2).

Japanese Patent Application Laid-Open No. 2007-1000054 JP 2004-169617 A

However, in the two-stage compression type rotary compressor having an internal intermediate pressure structure as described in Patent Document 2, for example, an oil separator is externally attached. Since piping is required, the size is increased and the cost is increased.

The same applies to a multistage compression rotary compressor having an internal intermediate pressure structure having a rotary compression element over three stages or a compression rotary compressor having an internal low pressure structure having a single rotary compression element. And has the same disadvantages.

Therefore, in view of the above-described circumstances, the present invention can provide a highly efficient compression function without cost, and can simultaneously reduce the installation space. An object of the present invention is to provide a rotary compressor.

A multistage compression rotary compressor according to claim 1 of the present invention is a multistage compression rotary compressor that is sandwiched between upper and lower support members via a drive element and an intermediate partition plate in a hermetic container and driven by the drive element. Each rotational compression element, and each rotational compression element of each stage includes a cylinder, a roller that is fitted to a rotation shaft of the drive element and rotates eccentrically in the cylinder, and abutting against the roller and the cylinder A vane that divides the inside into a low-pressure chamber and a high-pressure chamber, and is compressed by the rotary compression element of each stage, and the intermediate-pressure refrigerant gas discharged into the hermetic container is discharged to the rotary compression element of the final stage. In a multi-stage compression rotary compressor with an internal medium pressure structure that sucks in, compresses and discharges,
A spring for branching from a part of the refrigerant gas path for pressing the vane of the final stage rotary compression element, wherein the refrigerant gas discharged from at least the refrigerant discharge side of the final stage rotary compression element is sent out of the sealed container; While having a bypass passage communicating with the accommodated spring chamber,
In order to return the oil mixed in the refrigerant gas, which has been fed into the spring chamber together with the refrigerant gas through the bypass path, to the space in the sealed container, the inlet is moved forward toward the roller. Is provided, and the spring chamber is provided with a recovery path connected to the space in the sealed container.

According to a second aspect of the present invention, in the first aspect of the invention, the bypass path is provided inside the upper support member directly above the cylinder of the rotary compression element in the final stage.
The recovery path is provided inside the intermediate partition plate, directly below the cylinder of the rotary compression element of the final stage, having a substantially L-shaped cross section when cut in the thickness direction. It is characterized by.

A multistage compression rotary compressor according to a third aspect of the present invention includes a first element and a first element which are sandwiched between a drive element and upper and lower support members via an intermediate partition plate in a hermetic container and driven by the drive element. Two rotary compression elements, and the second rotary compression element includes a cylinder, a roller that is fitted to an eccentric portion formed on a rotation shaft of the drive element and rotates eccentrically in the cylinder, The intermediate pressure refrigerant gas that is composed of a vane that abuts on a roller and divides the inside of the cylinder into a low-pressure chamber and a high-pressure chamber, is compressed by the first rotary compression element, and is discharged into the hermetic container. In a multi-stage compression rotary compressor having an internal intermediate pressure structure that sucks, compresses and discharges the second rotary compression element,
A spring that branches off from a part of the refrigerant gas path where the refrigerant gas discharged from the refrigerant discharge side of the second rotary compression element is sent out of the sealed container and presses the vane of the second rotary compression element Including a bypass passage communicating with the spring chamber in which the
In order to return the oil mixed in the refrigerant gas, which has been sent to the spring chamber together with the refrigerant gas through the bypass, to the space in the sealed container, the vanes of the second rotary compression element are provided. When it advances toward the roller, the inlet is opened, and the spring chamber is provided with a recovery path connected to the space in the sealed container,
The recovery path is characterized in that when the vane advances to a predetermined position, the recovery inlet that has been blocked by the vane is opened and the oil that has been fed into the spring chamber is recovered into the space in the sealed container. To do.

According to a fourth aspect of the present invention, in the third aspect of the present invention, the bypass path is provided inside the upper support member directly above the cylinder of the second rotary compression element, and the recovery path is thick. What has a substantially L-shaped cross section is provided inside the intermediate partition plate directly below the cylinder of the second rotary compression element.

A compression-type rotary compressor according to claim 5 of the present invention includes a drive element and a single rotary compression element driven by the drive element in an airtight container. A cylinder sandwiched between members, a roller fitted into an eccentric portion formed on a rotation shaft of the drive element and rotated eccentrically in the cylinder, and a low pressure chamber and a high pressure chamber in contact with the roller and in the cylinder And compresses and discharges the low-pressure refrigerant gas in the sealed container of the rotary compression element, and the pressure on the refrigerant discharge side of the rotary compression element is applied as the back pressure of the vane. In a compression type rotary compressor having an internal low pressure structure,
The refrigerant gas discharged from the refrigerant discharge side of the rotary compression element is branched out from a part of the refrigerant gas discharge path where the refrigerant gas is sent out of the hermetic container, and communicates with a spring chamber containing a spring that presses the vane of the rotary compression element. With a bypass,
In order to return the oil mixed in the refrigerant gas, which is fed together with the refrigerant gas for back pressure through the bypass path, to the space in the sealed container, and collect the oil toward the roller. An inlet is opened when it moves forward, and the spring chamber is provided with a recovery path connected to the space in the sealed container.

According to a sixth aspect of the invention, in the fifth aspect of the invention, the bypass path is provided inside the upper support member directly above the cylinder of the rotary compression element,
The recovery path is characterized in that a section having a substantially L-shaped cross section in the thickness direction is provided inside the lower support member immediately below the cylinder of the rotary compression element.

According to the multi-stage compression rotary compressor according to claim 1 of the present invention, by providing a recovery path that opens and connects with the space in the sealed container only when the vane that contacts the outer periphery of the roller advances toward the roller, A highly efficient compression function can be realized without cost. At the same time, this enables oil to be collected inside the rotary compressor's sealed container without the need for an oil separator and external piping for oil return, thus reducing installation space. There is an advantage that a multi-stage compression type rotary compressor is obtained.

According to claim 2 of the present invention, a recovery path is provided inside the intermediate partition plate directly below the cylinder of the rotary compression element of the final stage, in which the cross section when cut in the thickness direction is substantially L-shaped. Thus, it is not necessary to separately install a dedicated piping path, and there is an advantage that downsizing can be achieved.

According to the multistage compression rotary compressor according to claim 3 of the present invention, by providing a recovery path that opens and connects with the space in the sealed container only when the vane that contacts the outer periphery of the roller advances toward the roller, A highly efficient compression function can be realized without cost. At the same time, this enables oil to be collected inside the rotary compressor's sealed container without the need for an oil separator and external piping for oil return, thus reducing installation space. There is an advantage that a two-stage compression type rotary compressor is obtained.

Further, according to claim 4 of the present invention, the recovery path is disposed inside the intermediate partition plate directly under the cylinder of the second stage rotary compression element in which the cross section when cut in the thickness direction is substantially L-shaped. By providing, it is unnecessary to separately install a dedicated piping path, and there is an advantage that downsizing can be achieved.

According to the multistage compression rotary compressor according to claim 5 of the present invention, by providing a recovery path that opens and connects with the space in the sealed container only when the vane that contacts the outer periphery of the roller advances toward the roller, A highly efficient compression function can be realized without cost. At the same time, this enables oil to be collected inside the rotary compressor's sealed container without the need for an oil separator and external piping for oil return, thus reducing installation space. There is an advantage that a one-stage compression type rotary compressor is obtained.

According to claim 6 of the present invention, a pipe having a substantially L-shaped cross section in the thickness direction is provided by providing a recovery path in the lower support member directly below the cylinder of the rotary compression element. Since there is no need to separately install the device, there is an advantage that downsizing can be achieved.

It is sectional drawing which shows the internal structure of the multistage compression type rotary compressor which concerns on embodiment of this invention. It is an expanded sectional view which shows the principal part. It is a bottom view which shows a state when the cylinder of the 1st rotation compression element is seen from the lower side. (A) And (B) is a top view which shows the cylinder, intermediate | middle partition plate, etc. of a 2nd rotation compression element, and its principal part enlarged view. (A) And (B) is explanatory drawing which shows the advance state of the vane in the cylinder of a 2nd rotation compression element, and its sectional drawing. (A) And (B) is explanatory drawing which shows the retreating state of the vane in the cylinder of a 2nd rotation compression element, and its sectional drawing. It is sectional drawing which shows the structure of the conventional two-stage compression type rotary compressor. It is a top view which shows the principal part of the lower cylinder of the compression type rotary compressor shown in FIG.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
FIG. 1 shows a main part of a multi-stage compression rotary compressor 1 according to an embodiment of the present invention. The multi-stage compression rotary compressor 1 is composed of a rotor 22 and a stator 23 in a hermetic container 1A. The electric element 2 which comprises an element, the 1st rotation compression element 3 and the 2nd rotation element 4 which are driven with this electric element 2, and the intermediate partition plate 5 are provided.

The first and second

rotary compression elements

3 and 4 are fitted to flat and substantially disk-shaped

cylinders

31 and 41 and

eccentric parts

32 and 42 formed eccentrically on the rotary shaft 21 of the electric element 2.

Rollers

33, 43 that rotate eccentrically inside the

cylinders

31, 41,

vanes

34, 44 that abut against the

rollers

33, 43 and divide the

cylinders

31, 41 into low pressure chambers and high pressure chambers, and

support members

35, 45 And each.

Among these, a cylinder (hereinafter referred to as a “lower cylinder”) 31 that constitutes a part of the first rotary compression element 3 has an abbreviation as a space in which the roller 33 rotates eccentrically as shown in FIG. From the vane chamber 311 to accommodate a cylinder chamber 310 formed of a perfect circular space, a narrow groove-shaped vane chamber 311 for accommodating the vane 34, and a spring 36 for pressing the vane 34 inside the vane chamber 311 from the back surface. A spring chamber 312 comprising a partially opened vertical hole 312A formed of a wide space and a horizontal hole 312B provided in a tunnel shape inside the cylinder so as to communicate between the vertical hole 312A and the outer peripheral surface 31A of the lower cylinder 31. And a plug 313 that closes the inlet opening in the outer peripheral surface 31 A of the spring chamber 312.

In this embodiment, the cylinder chamber 310 and the vane chamber 311 are formed so as to penetrate to both the upper and lower surfaces of the lower cylinder 31 having a substantially disk shape. In this way, each of the above-described chambers is opened so as to penetrate in the same shape in the upper and lower sides, but after inserting the roller 33 and the vane 34 into each chamber, the upper and lower surfaces of the lower cylinder 31 are supported by the intermediate partition plate 5 and the support. Since it is clamped by the member 35, it does not fall off.

The spring chamber 312 includes a vertical hole 312A that opens to the lower surface of the lower cylinder 31 and a horizontal hole 312B that communicates therewith and penetrates to the outer peripheral surface 31A of the lower cylinder 31. That is, the vertical hole 312 A is formed so as to be wider than the vane chamber 311 and continuous with the vane chamber 311 and to be opened to the upper surface side of the lower cylinder 31. Thus, the intermediate pressure state filled in the sealed container 1A through the shallow groove 35B provided on the upper surface side of the support member (hereinafter referred to as “lower support member”) 35 on the first rotary compression element 3 side. This refrigerant gas can enter the inside of the spring chamber 312.

On the other hand, the horizontal hole 312B is formed in a tunnel shape inside the cylinder 31 so as to communicate between the above-described vertical hole 312A and the outer peripheral surface 31A of the lower cylinder 31, and the spring 36 is connected to the deep vertical hole. After the insertion up to 312A, the plug 313 is press-fitted to close the inlet opened in the outer peripheral surface 31A.

Further, as shown in FIG. 3, the lower cylinder 31 has been refluxed into the sealed container 1 A of the rotary compressor 1 via a required refrigeration cycle (not shown) externally connected to the sealed container 1 A of the rotary compressor 1. The suction hole 314 for allowing the refrigerant gas in the low pressure state to be taken into the cylinder chamber 310 again, and the refrigerant gas pressurized in the cylinder chamber 310 to the intermediate pressure state are taken out from the cylinder chamber 310 and the second rotary compression element 4 A discharge hole 315 for feeding into the cylinder chamber 310 is opened on the inner peripheral surface of the cylinder chamber 310.

The suction hole 314 and the discharge hole 315 communicate with the suction port 314A and the discharge port 315A, respectively. The suction port 314A is connected to a refrigerant circuit of a refrigeration cycle (not shown) outside the rotary compressor 1 via a suction passage (not shown). The discharge port 315 A communicates with the inside of the sealed container 1 A of the rotary compressor 1.

The roller 33 rotates about one rotation while being eccentric in the cylinder chamber 310 of the lower cylinder 31, thereby compressing the refrigerant sucked into the cylinder chamber 310 from the low pressure state at the beginning of suction to the intermediate pressure state at the time of discharge. It is what you want to do. Although the outer shape of the roller 33 of the present embodiment is a perfect circle, the roller 33 is fixed to an eccentric portion 32 provided in an eccentric state on the rotary shaft 21 and rotates inside the cylinder chamber 310 in an eccentric state.

The vane 34 is configured by a thin plate having a substantially rectangular vertical cross section and standing in the vertical direction. The base end surface is pressed by the spring 36, and the distal end surface is pressed by the elastic force of the spring 36. Is always in close contact with the outer periphery of the.

The lower support member 35 of the present embodiment supports the lower cylinder 31 from the lower side and holds the lower cylinder 31 in close contact with the intermediate partition plate 5 disposed in close contact with the upper side of the lower cylinder 31. As shown in FIGS. 1 and 2, the lower support member 35 includes the lower silencing chamber 35 A shown in FIG. 2, in addition to the lower silencing chamber 35 A that takes in and silences the intermediate pressure refrigerant discharged from the cylinder chamber 310. The groove 35 B communicates with the vertical hole 312 A which is a part of the spring chamber 312, and is formed to reach the outer peripheral surface.
The vertical hole 312A may be configured to open only on the lower surface side so as to lie from the lower surface side of the lower cylinder 31. However, in the present embodiment, as described above, the vertical hole 312A is opened through both the upper and lower surfaces. It is.

The spring 36 uses a compression coil spring, and is always kept in a compressed state even if it is housed in the spring chamber 312. Therefore, the spring 36 having a natural length longer than the longitudinal dimension of the spring chamber 312 is used. Thereby, even when the spring 36 is accommodated in the spring chamber 312 and extends to the maximum, the spring 36 can obtain an action that can surely bias the elastic force that presses the vane 34.

On the other hand, a cylinder (hereinafter referred to as “upper cylinder”) 41 constituting a part of the second rotary compression element is similar to the lower cylinder 31 of the first rotary compression element as shown in FIG. In addition, a cylinder chamber 410 formed of a substantially circular space in which the roller 43 rotates eccentrically, a vane chamber 411 having a narrow groove shape for accommodating the vane 44, and a spring 46 that presses the vane 44 inside the vane chamber 411 from the back surface. A spring chamber 412 that is wider than the vane chamber 411, a suction hole 414 that allows the intermediate pressure refrigerant compressed by the first rotary compression element 3 to be taken into the cylinder chamber 410, and a cylinder A discharge hole 41 for taking out the refrigerant gas pressurized in the chamber 410 from the cylinder chamber 410 and discharging it from the refrigerant discharge pipe (not shown) to the outside of the rotary compressor 1. And, it is provided.

Further, the spring chamber 412 provided in the upper cylinder 41 is constituted by a vertical hole 412A and a horizontal hole 412B, similarly to the spring chamber 312 of the first rotary compression element 3.
Among them, the vertical hole 412A has a perfect circular shape as shown in FIG. 4 as shown in FIG. 5A, as in the lower cylinder 31 of the first rotary compression element 3, as shown in FIG. The upper cylinder 41 is penetrated so as to reach from the upper surface to the lower surface. In this way, the vertical hole 412A is opened so as to penetrate both the upper and lower surfaces of the upper cylinder 41 because the outlet 451 of the bypass passage 45B formed in the support member 45 described later and the upper surface side of the vertical hole 412A. This is because the opening 51A of the collecting path 51 of the intermediate partition plate 5 described later and the opening part on the lower surface side of the vertical hole 412A are communicated. The state of communication between the collection port 51A of the collection path 51 of the intermediate partition plate 5 and the opening portion on the lower surface side of the vertical hole 412A will be described in detail later.

On the other hand, the horizontal hole 412B communicates between the above-described vertical hole 412A and the outer peripheral surface 41A of the upper cylinder 41 in the same manner as the horizontal hole 312B of the spring chamber 312 of the first rotary compression element 3. 41 is formed in a tunnel shape so as to penetrate to the outer peripheral surface 41 A of the upper cylinder 41. The horizontal hole 412B is configured such that after the spring 46 is inserted from the hole opened in the outer peripheral surface 41A of the upper cylinder 41 to the vertical hole 4121A at the back, the plug 413 is press-fitted and the inlet of the hole is blocked. ing.

Thus, the upper cylinder 41 of the present embodiment is also provided with the cylinder chamber 410, the vane chamber 411, and the spring chamber 412 so as to penetrate both the upper and lower surfaces. Among the spring chambers 412, the vertical holes 412 A need to open through both the upper and lower surfaces of the upper cylinder 41. By configuring the vertical hole 4121A in this way, communication with a bypass path 45B inside the upper support member 45 described later and communication with the collection path 51 inside the intermediate partition plate 5 are ensured. The vane chamber 411 may have a configuration in which only the lower surface side is opened without opening up to the upper surface of the upper cylinder 41, and the vane chamber 411 extends in the thickness direction.

A support member (hereinafter referred to as “upper support member”) 45 according to the present embodiment is in close contact with the upper surface side of the upper cylinder 41 from above, and an intermediate partition plate provided on the lower side of the upper cylinder 41. The upper cylinder 41 is sandwiched between the upper cylinder 41 and the upper cylinder 41. In addition to the upper silencing chamber 45A that takes in and silences the high-pressure refrigerant discharged from the cylinder chamber 410, the upper supporting member 45 is compressed into a high pressure state and is silenced as shown in FIGS. In order to introduce a part of the refrigerant gas discharged to 45A into the spring chamber 412 of the upper cylinder 41 and apply it as a back pressure of the vane, a tunnel-like bypass circuit 45B (which constitutes a part of the silencing chamber) is provided in the spring chamber 412. It is formed inside so as to communicate.

In the intermediate partition plate 5, a recovery path 51 having a recovery inlet 51 A that can communicate with the opening is formed in a portion corresponding to the lower opening of the vertical hole 412 A of the spring chamber 412 of the upper cylinder 41. .

The recovery path 51 of the present embodiment has a substantially L-shaped cross section when the intermediate partition plate 5 is cut in the thickness direction. As shown in FIG. The spring chamber 412 has an opening immediately below it so as to face the lower surface side opening of the vertical hole 412A. Further, a recovery outlet 51B is opened on the outer peripheral surface of the intermediate partition plate 5 and communicates with the space in the sealed container 1A.

The recovery inlet 51A of the present embodiment has a perfect circle shape, but may be, for example, an inverted triangle that gradually expands along the forward direction in which the vane 44 advances, a triangle that gradually decreases, or the like along the front direction. In this case, the oil discharge amount may be adjusted in accordance with the advance position of the vane 44. Further, the recovery inlet to be opened in the intermediate partition plate 5 at a portion immediately below the recovery path 51 provided facing the lower surface side opening of the vertical hole 412A of the spring chamber opens in a long hole groove shape or the like. May be.

That is, as shown in FIG. 5, when the vane 44 accommodated in the vane chamber 411 of the upper cylinder 41 is advanced to a predetermined position, the recovery path 51 is provided with a recovery inlet 51A sealed by the vane 44. Opens. For this reason, the oil that has been fed into the spring chamber 412 is collected from the opened collection inlet 51A into the space inside the sealed container 1A. On the other hand, as shown in FIG. 6, when the vane 44 moves backward from the predetermined position, the recovery inlet 51 A is closed by the vane 44 and closed. The opening position of the recovery inlet 51A may be a portion corresponding to the lower opening at the boundary between both the vane chamber 411 and the vertical hole 412A.

Next, a compression operation in two stages, which is a basic operation in the multistage compression rotary compressor 1 of the present embodiment, will be described with reference to the drawings.
In FIG. 1, when a coil (not shown) on the stator 23 side of the electric element 2 of the compressor 1 is energized via a wiring (not shown), the electric element 2 is activated and the rotor 22 rotates. Due to this rotation, the upper and

lower rollers

33 and 43 which are fixed integrally with the rotary shaft 21 and fit into the lower

eccentric portions

32 and 42 are respectively in the

cylinder chambers

310 and 410 of the upper and

lower cylinders

31 and 41. The inside rotates eccentrically.

Thus, the low pressure chamber (in FIG. 3) of the cylinder chamber 310 from the suction port 314A (see FIG. 3) of the lower cylinder 31 via the refrigerant introduction pipe (not shown) and the suction passage (not shown) formed in the lower support member 35. The low-pressure refrigerant gas sucked into the upper space) side is compressed by the operation of the roller 33 and the vane 34 to become an intermediate pressure, and enters the sealed container 1A from the high-pressure chamber side of the lower cylinder 31 through the discharge port 315A and the sound deadening chamber 35A. Discharged. Thus, the first stage compression operation is performed, and the inside of the sealed container 1A becomes an intermediate pressure.

The intermediate-pressure refrigerant gas discharged into the sealed container 1A is deprived of heat and cooled in the sealed container 1A.

Then, the refrigerant gas in the intermediate pressure state passes through a suction passage (not shown) formed in the upper support member 45 from the suction port 414A of the upper cylinder 41 of the second rotary compression element 4 shown in FIG. 410 is sucked into the low pressure chamber side (upper space in FIG. 4A), and the compression operation of the second stage is performed by the operation of the roller 43 and the vane 44 (the compression process of one cycle is FIG. 5 → FIG. 6 → FIG. 5). Is done. As a result, the refrigerant gas enters a high pressure and high temperature state shown in FIG. 5, passes through the discharge port 415A from the high pressure chamber side, passes through the discharge silencer chamber 45A formed in the upper support member 45, and is closed by the refrigerant discharge pipe (not shown). To the external piping (refrigerant circuit).

Next, in the

upper cylinders

31 and 41 according to the present invention, operations of the

spring chambers

312 and 412 and the refrigerant gas and oil introduced therein will be mainly described.
In the cylinder chamber 310 of the lower cylinder 31 of the first rotary compression element 3, the roller 33 that rotates eccentrically for the first-stage compression operation starts from the initial state where the low-pressure refrigerant gas is sucked into the low-pressure chamber shown in FIG. The refrigerant gas is compressed to an intermediate pressure in the chamber (this low-pressure chamber eventually becomes a high-pressure chamber) until the final state of cold discharge. In order to hold the refrigerant gas in a sealed state inside the cylinder chamber 310 into which the refrigerant gas is introduced during this one cycle, in other words, in order to separate the low pressure chamber and the high pressure chamber, the cylinder chamber 310 It is important to make the tip of the vane 34 firmly contact the inner roller 33.

Therefore, in order to press the vane 34 against the outer peripheral surface of the roller 33, as described above, the vane 34 is pressed from the back by the spring 36 accommodated in the spring chamber 312, and the vane 34 is pressed by the elastic force of the roller 33. It is in pressure contact with the outer peripheral surface. However, in the lower cylinder 31 of the first rotary compression element 3, as described above, the refrigerant gas is compressed to the intermediate pressure state by the first-stage compression operation. For this reason, the pressing force to the vane 34 does not require a large force as much as the pressing force required to act on the vane in the second rotary compression element 4. In other words, the compression is not performed up to the high pressure compression like the second stage compression operation in the second rotary compression element 4.

Due to such circumstances, the longitudinal hole 312A passes through the shallow groove 35B that allows the intermediate pressure refrigerant gas filled in the sealed container 1A of the rotary compressor 1 to communicate between the spring chamber 312 and the sealed container 1 inside. It is sufficient to take in the inside of the spring chamber 312 from the opening and apply the gas pressure to the vane 34 additionally. Therefore, in the first rotary compression element 3, the oil suction operation as described above is performed as shown in FIG.

Next, the refrigerant gas that fills the sealed container 1A of the rotary compressor 1 causes the intermediate pressure in the first rotary compression element 3 to remain inside the sealed container 1A as it is without passing through piping outside the sealed container 1A. Introduced into the second rotary compression element 4. In addition, since there is a thing which requires cooling of intermediate gas depending on a use etc., in this invention, the structure via an external piping may be sufficient.

Also in the cylinder chamber 410 of the upper cylinder 41 of the second rotary compression element 4, as shown in FIGS. 5 and 6, the second stage compression operation is performed through the same process, and the refrigerant gas in the intermediate pressure state is obtained. Is compressed to a high pressure state. For this reason, in order to cope with the high pressure compression state that is the final pressure inside the cylinder chamber 410, in addition to the elastic force by the spring 46 that presses the vane 44, the pressure of the high-pressure refrigerant gas is used inside the spring chamber 410. The vane 44 is additionally pressed.

That is, it is formed inside the upper support member 45 so as to communicate from the upper silencing chamber 45A from which the refrigerant gas compressed to a high pressure state is discharged from the cylinder chamber 410 to the opening portion of the vertical hole 412A of the spring chamber 412. A part of the high-pressure refrigerant gas is introduced into the spring chamber 412 through the bypass passage 45B and the opening of the vertical hole 412A. Thereby, the refrigerant gas introduced into the spring chamber 412 is applied as the back pressure of the vane 44.

By the way, the refrigerant gas that has been compressed in the second stage and compressed from the intermediate pressure state to the high pressure state passes through the discharge port 415A from the high pressure chamber side inside the cylinder chamber 410 and passes through the upper support member 45 as described above. After passing through the discharge silencing chamber 45A, the refrigerant is discharged to an external pipe (refrigerant circuit) of the sealed container 1A by a refrigerant discharge pipe (not shown). In this case, although the refrigerant gas depends on the type of the gas, for example, in the case of carbon dioxide gas or the like, the refrigerant gas is greatly increased in pressure until a differential pressure of about Δ8 MPa (for example, 5 MPa → 13 MPa). When the differential pressure is large, a large amount of oil is required as a seal material to prevent leakage inside and outside the compression chamber. Generally, however, the supplied oil is hermetically sealed in internal low-pressure and internal / intermediate-pressure compressors. The oil amount in the refrigeration cycle increased because it was discharged directly to the external piping without being separated and reused inside the container 1A.

Therefore, in the present invention, as described above, the recovery path 51 having the recovery inlet 51A that can communicate with the lower opening of the vertical hole 412A of the spring chamber 412 is formed inside the intermediate partition plate 5.

That is, the refrigerant gas that has been compressed from the lower cylinder 31 of the first rotary compression element 3 to the intermediate pressure state moves forward as the vane 44 moves forward from a predetermined position as shown in FIG. The internal space of the chamber 411 increases. Then, as the internal space of the vane chamber 411 increases, the internal pressure of the spring chamber 412 communicating with the vane chamber 411 decreases, so that the silencing chamber 45A in the high pressure state of the upper cylinder 41 of the second rotary compression element 4 Differential pressure is generated during

As a result, due to this differential pressure, as shown in FIG. 5B, the interior of the sound deadening chamber 45A is moved from the suction port 414A of the upper cylinder 41 of the second rotary compression element 4 toward the spring chamber 412 of the upper cylinder chamber 41. Refrigerant gas and oil mixed therein flow in via the bypass passage 45B. As a result, as described above, when the internal pressure of the spring chamber 412 increases, the pressure of the high-pressure refrigerant gas is applied to the back surface of the vane 44 together with the elastic force of the spring 46 using this high-pressure refrigerant gas. Is done.

At this time, as shown in FIG. 5 (A), the cylinder chamber 410 has a high-pressure chamber (lower space in FIG. 5 (A)), which is a space divided into two by the vane 44. The refrigerant gas enters a high-temperature and high-pressure state, passes through the discharge port 415A from the high-pressure chamber side, passes through the discharge silencer chamber 45A formed in the upper support member 45, and is connected to the external pipe (refrigerant circuit) of the sealed container 1A by a refrigerant discharge pipe (not shown). However, the mixture of oil is suppressed as much as possible in the refrigerant gas.

That is, in the state shown in FIG. 5 (A), the recovery inlet of the recovery path 51 that has been blocked by the vane 44 up to the opening portion on the lower side of the vertical hole 412A of the spring chamber 412 in a high pressure state. 51A is released by the forward movement of the vane 44. For this reason, the spring chamber 412 in a high pressure state communicates with the inside of the recovery path 51 of the intermediate partition plate 5. On the other hand, the recovery outlet 51 B of the recovery path 51 is in a communication state that is always open to the inside of the sealed container 1 A of the rotary compressor 1.

Accordingly, the oil in the spring chamber 412 and further the second rotary compression element 4 are utilized by utilizing the differential pressure from the vertical hole 412A of the spring chamber 412 in the high pressure state toward the inside of the sealed container 1A in the intermediate pressure state. Even the oil in the silencing chamber 45A in the high pressure state of the upper cylinder 41 is discharged. Thus, most of the oil mixed in the refrigerant gas discharged from the closed container 1A through the discharge silencer chamber 45A to the outside of the sealed container 1A is not discharged to the outside of the sealed container 1A. Before being discharged from the sealed container 1A to the outside, it is recovered inside the sealed container 1A.

Therefore, conventionally, most of the oil that has been discharged to the outside of the sealed container 1A by a refrigerant discharge pipe (not shown) may be leaked to the refrigeration cycle outside the sealed container 1A according to this embodiment. Effectively suppressed. As a result, the refrigeration effect is enhanced, and the oil replenishment amount and replenishment frequency that have been reduced by leaking into the refrigeration cycle can be reduced.

Further, conventionally, it has been required when the amount of oil leaked into the refrigeration cycle is so large that it cannot be ignored. Therefore, oil separation means such as an oil separator attached to the sealed container 1A and installed outside and oil return According to the present embodiment, the installation of the piping for use can be omitted. For this reason, the installation space can be reduced by that amount, and the cost can be reduced.

It should be noted that the present invention is not limited to the above embodiment, and various modifications can be made without departing from the scope of the claims.

In other words, in the present embodiment, the multi-stage compression rotary compressor is composed of upper and lower two-stage rotary compression elements, but a multi-stage compression rotary compressor composed of three or more stages of rotary compression elements may be used. In that case, a recovery path may be provided at least in the intermediate partition plate interposed between the rotary compression element at the final stage and the rotary compression element at the next stage. On the other hand, a bypass path is provided in the upper support member directly above the final stage rotary compression element.

Furthermore, in the present invention, a configuration having a single rotary compression element may be used. In this case, a recovery path may be provided in the lower support member of the upper and lower support members that sandwich the cylinder that is a part of the rotary compression element. On the other hand, a bypass path is provided in the upper support member.

DESCRIPTION OF SYMBOLS 1 Multistage compression type rotary compressor 1A Airtight container 22 Rotor 23 Stator 2 Electric element 21 Rotating shaft 3 1st rotation compression element 31 Lower cylinder 310,410 Cylinder chamber 311,411 Vane chamber 312,412 Spring chamber

312A Vertical hole

312B Horizontal hole

313, 413

Plug

32, 42

Eccentric part

33, 43

Roller

34, 44

Vane

35, 45

Support member

314, 414 Suction hole 314A Suction port 315 Ejection hole 315A

Discharge port

35B Shallow groove

36, 46 Spring 4 Second rotating element 41 Upper cylinder

412A Vertical hole

412B Horizontal hole 415 Discharge hole 45B Bypass path 451 Exit 5 Intermediate partition plate 51 Recovery path 51A Recovery port (inlet)
51B Recovery outlet

Claims

A sealed element is provided with a driving element and multistage rotary compression elements that are sandwiched between upper and lower support members via intermediate partition plates and driven by the driving element, respectively. The element includes a cylinder, a roller that is fitted to a rotation shaft of the drive element and rotates eccentrically in the cylinder, and a vane that abuts on the roller and divides the cylinder into a low pressure chamber and a high pressure chamber. A multi-stage structure having an internal / intermediate pressure structure in which the intermediate-pressure refrigerant gas compressed by the rotary compression element of each stage and discharged into the hermetic container is sucked into the rotary compression element of the final stage, and compressed and discharged. In compression type rotary compressor,
A spring for branching from a part of the refrigerant gas path for pressing the vane of the final stage rotary compression element, wherein the refrigerant gas discharged from at least the refrigerant discharge side of the final stage rotary compression element is sent out of the sealed container; While having a bypass passage communicating with the accommodated spring chamber,
In order to return the oil mixed in the refrigerant gas, which has been fed into the spring chamber together with the refrigerant gas through the bypass path, to the space in the sealed container, the inlet is moved forward toward the roller. Is provided, and the spring chamber is provided with a recovery path connected to the space in the sealed container,
A multi-stage compression rotary compressor characterized by that.
The bypass path is provided inside the upper support member directly above the cylinder of the rotary compression element of the final stage,
The recovery path is provided inside the intermediate partition plate, directly below the cylinder of the rotary compression element of the final stage, in which the cross section when cut in the thickness direction has a substantially L shape.
The multistage compression rotary compressor according to claim 1, wherein the multistage compression rotary compressor is provided.
In the sealed container, a drive element and first and second rotary compression elements sandwiched between upper and lower support members via an intermediate partition plate and driven by the drive element, the second rotation The compression element includes a cylinder, a roller that is fitted to an eccentric portion formed on a rotation shaft of the drive element and rotates eccentrically in the cylinder, and a low pressure chamber and a high pressure chamber that are in contact with the roller and are inside the cylinder. The refrigerant gas is compressed by the first rotary compression element and discharged into the hermetic container, and the intermediate pressure refrigerant gas is sucked into the second rotary compression element, compressed and discharged. In multi-stage compression rotary compressor with internal / intermediate pressure structure,
A spring that branches off from a part of the refrigerant gas path where the refrigerant gas discharged from the refrigerant discharge side of the second rotary compression element is sent out of the sealed container and presses the vane of the second rotary compression element Including a bypass passage communicating with the spring chamber in which the
In order to return the oil mixed in the refrigerant gas, which has been sent to the spring chamber together with the refrigerant gas through the bypass, to the space in the sealed container, the vanes of the second rotary compression element are provided. When it advances toward the roller, the inlet is opened, and the spring chamber is provided with a recovery path connected to the space in the sealed container,
In the recovery path, when the vane advances to a predetermined position, the recovery inlet that has been blocked by the vane is opened, and the oil that has been fed into the spring chamber is recovered into the space in the sealed container,
A multi-stage compression rotary compressor characterized by that.
The bypass path is provided inside the upper support member directly above the cylinder of the second rotary compression element,
The recovery path is provided inside the intermediate partition plate, directly below the cylinder of the second rotary compression element, in which the cross section in the thickness direction has a substantially L shape.
The multi-stage compression rotary compressor according to claim 3, wherein
The sealed container includes a drive element and a single rotary compression element driven by the drive element. The rotary compression element includes a cylinder sandwiched between upper and lower support members, and a rotation shaft of the drive element. A roller that is fitted to an eccentric portion formed in the cylinder and rotates eccentrically in the cylinder, and a vane that abuts the roller and divides the cylinder into a low pressure chamber and a high pressure chamber. In a compression type rotary compressor having an internal low-pressure structure, in which a low-pressure refrigerant gas is compressed and discharged in a sealed container of the element, and a pressure on the refrigerant discharge side of the rotary compression element is applied as a back pressure of the vane.
The refrigerant gas discharged from the refrigerant discharge side of the rotary compression element is branched out from a part of the refrigerant gas discharge path where the refrigerant gas is sent out of the hermetic container, and communicates with a spring chamber containing a spring that presses the vane of the rotary compression element. With a bypass,
In order to return the oil mixed in the refrigerant gas, which is fed together with the refrigerant gas for back pressure through the bypass path, to the space in the sealed container, and collect the oil toward the roller. An inlet is opened when moving forward, and the spring chamber has a recovery path connected to the space in the sealed container;
A compression-type rotary compressor characterized by that.
The bypass path is provided inside the upper support member directly above the cylinder of the rotary compression element,
The recovery path has a substantially L-shaped cross section in the thickness direction, and is provided inside the lower support member directly below the cylinder of the rotary compression element.
The compression type rotary compressor according to claim 5, wherein