JP7678527B2 - Rotary compressor and refrigeration cycle device - Google Patents

Description

This disclosure relates to rotary compressors and refrigeration cycle devices in which they are used, such as air conditioners, freezers, blowers, and water heaters.

Patent Document 1 discloses a rotary compressor that reliably prevents vane jumping. This rotary compressor includes a cylinder whose openings at both ends are closed, a piston that rotates within the cylinder, a vane that forms a compression space with the piston and cylinder and separates the high-pressure side from the low-pressure side, and a connecting means that connects the piston and vane so that they can swing freely.

JP 2000-120572 A

The present disclosure provides a rotary compressor and refrigeration cycle device that reduces leakage loss by lowering the cylinder height and ensures the cross-sectional area of the suction passage to suppress an increase in pressure loss.

The rotary compressor and refrigeration cycle device disclosed herein comprises a drive shaft having an eccentric shaft, a piston fitted to the eccentric shaft, a cylinder housing the eccentrically rotating piston, upper and lower end plates closing the upper and lower opening faces of the cylinder, a vane dividing the space formed by the cylinder, the piston and the upper and lower end plates into a suction chamber and a compression chamber and moving integrally with the piston, and an intake hole provided in at least one of the upper and lower end plates to which an intake pipe is connected for introducing intake gas from outside the compressor into the suction chamber.

In the rotary compressor and refrigeration cycle device disclosed herein, the cylinder height can be reduced by increasing the cylinder inner diameter. This reduces the leakage gap cross-sectional area of the seal between the cylinder inner circumference and the piston outer circumference, reducing leakage loss and improving compressor efficiency. In addition, since the suction passage is provided in either the upper or lower end plate, the suction passage area can be secured and an increase in pressure loss in the suction passage can be suppressed.

FIG. 1 is a vertical cross-sectional view of a rotary compressor according to a first embodiment of the present invention. FIG. 1 is a cross-sectional view of a compression mechanism according to a first embodiment of the present invention. FIG. 2 is an explanatory diagram of a compression operation of the compression mechanism according to the first embodiment of the present invention; FIG. 11 is a vertical sectional view of a rotary compressor according to a second embodiment of the present invention. FIG. 11 is a vertical sectional view of a rotary compressor according to a third embodiment of the present invention.

(The knowledge and other information that formed the basis of this disclosure)
At the time when the inventors came up with the idea of this disclosure, a rotary compressor had a spring on the back of the vane, and the vane was pressed against the piston by the force of the spring and the pressure difference, and the pressing of the vane formed a compression chamber to perform compression. However, the above-mentioned conventional rolling piston type rotary compressor had a problem of so-called vane jumping due to insufficient pressing force under load conditions such as low compression ratio. Therefore, the rolling piston type had problems of noise deterioration due to the vane colliding with the piston and performance deterioration due to leakage in the gap between the vane and the piston.

For this reason, a technology has been proposed to prevent vane jumping by connecting the piston and vane so that they can swing freely and move together to perform compression. This not only solves the above-mentioned problem, but also eliminates the need for a spring to press the vane, making it possible to eliminate the need for a spring, reducing assembly labor by reducing the number of parts, and directly reducing material costs.

In rotary compressors, where the piston and vanes move together to perform compression, there is no need for space to accommodate springs, so the vanes can be positioned further out than in the former rolling piston type. As a result, this rotary compressor can have a larger cylinder inner diameter and a lower cylinder height. This reduces the cross-sectional area of the leakage gap in the seal between the outer periphery of the piston and the inner periphery of the cylinder, reducing leakage losses.

However, when the cylinder height is reduced, the diameter of the intake passage, which is located on the outer periphery of the cylinder and introduces intake gas from outside the compressor, becomes smaller, and the cross-sectional area of the intake passage cannot be secured sufficiently. This causes an increase in pressure loss during the intake process, which in turn worsens the efficiency of the compressor.

The inventors discovered this problem and came up with the subject matter of the present disclosure to solve it.

Therefore, the present disclosure provides a rotary compressor that reduces leakage loss by lowering the cylinder height and ensures the cross-sectional area of the suction passage to suppress an increase in pressure loss.

Below, the embodiments will be described in detail with reference to the drawings. However, more detailed explanation than necessary may be omitted. For example, detailed explanations of matters that are already well known, or duplicate explanations of substantially identical configurations may be omitted. This is to avoid making the following explanation unnecessarily redundant and to make it easier for those skilled in the art to understand.

It should be noted that the accompanying drawings and the following description are provided to enable those skilled in the art to fully understand the present disclosure and are not intended to limit the subject matter described in the claims.

(Embodiment 1)
Hereinafter, the first embodiment will be described with reference to FIGS. 1 to 3. FIG.

[1-1. Configuration]
In Figures 1 and 2, rotary compressor 100 includes a drive shaft 101, a piston 102, a cylinder 103, an upper end plate (hereinafter referred to as the upper bearing) 104 functioning as an upper bearing, a lower end plate (hereinafter referred to as the lower bearing) 105 functioning as a lower bearing, a vane 106, and a suction hole 107a.

The entire interior of the sealed container 108 is a discharge pressure atmosphere that communicates with the discharge pipe 109. The electric motor 110 is housed in the center of the sealed container 108, and the compression mechanism 111 is housed in the lower part. The compression mechanism 111 is driven by a drive shaft 101 fixed to the rotor 110a of the electric motor 110.

This compression mechanism 111 is configured to sandwich the cylinder 103, piston 102 and vane 106 between an upper bearing 104 and a lower bearing 105, and to perform compression operation by forming a suction chamber 112 and a compression chamber 113 by dividing the space formed between the cylinder 103 and the piston 102 with the vane 106.

An eccentric shaft 101a that is integral with the drive shaft 101 is housed inside the cylinder 103, and a piston 102 is rotatably attached to this eccentric shaft 101a. An engagement groove 102a is formed on the outer periphery of the piston 102, and a vane 106 with an engagement portion 106a formed on the tip side is connected to the piston 102 so that it can swing freely. There is no spring provided on the back side of the vane 106 as in the conventional rolling piston type.

The upper bearing 104 is provided with an intake passage 107 consisting of a radial intake hole 107a and an axial vertical hole 107b, which communicates with the intake chamber 112. An intake liner 114 is press-fitted into the intake hole 107a. The intake liner 114 separates the high-temperature, high-pressure discharge gas inside the sealed container 108 from the low-temperature, low-pressure intake gas inside the intake hole 107a.

An accumulator 115 is inserted into the suction liner 114 to prevent liquid compression in the compressor. The accumulator 115 is connected by brazing or welding to an outer suction pipe 116 fixed to the sealed container 108, and separates the working fluid sucked into the rotary compressor 100 into gas and liquid.

That is, in the first embodiment, the intake gas from outside the compressor is introduced into the intake chamber 112 through an intake pipe composed of an intake liner 114 into which the accumulator 115 is inserted and an intake outer pipe 116. The intake pipe may be composed of only the accumulator 115 and the intake outer pipe 116, and the accumulator 115 may be connected directly to the intake hole 107a.

In addition, the rotary compressor 100 of this embodiment uses, for example, carbon dioxide as a working fluid.

[1-2. Operation]
The operation of the rotary compressor 100 configured as above will be described below with reference to FIGS.

[1-2-1. Compression Operation]
3 is a diagram for explaining the change in volume of the suction chamber 112 and the compression chamber 113 for every 90 degrees of crank angle, and the volumes change in the directions of the outlined arrows. The suction passage 107 of the upper bearing 104 (not shown) is located to the left of the vane 106 and communicates with the suction chamber 112.

When the electric motor 110 is energized and the drive shaft 101 rotates, the eccentric shaft 101a rotates eccentrically within the cylinder 103, and the connected piston 102 and vane 106 move together. This causes the intake and compression of the working fluid to be repeated.

Low-temperature, low-pressure gas is sucked into the suction chamber 112 through the accumulator 115, the suction liner 114, and the suction passage 107. The low-temperature, low-pressure suction gas is compressed in the compression mechanism 111. The compressed high-temperature, high-pressure gas passes through a discharge hole (not shown) provided in the upper bearing 104 and communicating with the compression chamber 113, and is discharged into the muffler chamber 117 (see FIG. 1) through a check valve. The discharge gas then passes through a small hole provided in the muffler 118, the lower motor space 119 between the compression mechanism 111 and the electric motor 110, and each gap in the electric motor 110. The discharge gas is then guided to the upper motor space 120 and discharged from the rotary compressor 100 through the discharge pipe 109.

[1-2-2. Refueling operation]
Oil is stored in the lower part of the sealed container 108, and the compression mechanism 111 is usually immersed in the oil. An oil passage (not shown) is provided in the axial direction inside the drive shaft 101. The oil sucked up from the lower end of the oil passage passes through an oil supply hole (not shown) provided in the eccentric shaft 101a, and reaches the inner periphery of the piston 102 while lubricating the sliding parts of the eccentric shaft 101a. Then, one of the oils lubricates the journal bearing sliding parts of the upper bearing 104 and the lower bearing 105 and is discharged outside the compression mechanism 111, and the other of the oil is supplied to the suction chamber 112 and the compression chamber 113 while lubricating the sliding parts between the upper and lower end faces of the piston 102 and the upper bearing 104 and the lower bearing 105.

In addition, the oil supplied from the back of the vane 106 lubricates the sliding parts of the vane 106, and is then supplied to the suction chamber 112 and compression chamber 113. The oil inside the suction chamber 112 and compression chamber 113 is discharged from the discharge hole 121 together with the gas, and then rides the above-mentioned gas flow to reach the discharge pipe 109. During this time, most of the oil is separated from the discharged gas and turns into droplets, which return to the bottom of the sealed container 108 by gravity.

[1-3. Effects, etc.]
As described above, in this embodiment, the rotary compressor 100 includes the drive shaft 101, the piston 102, the cylinder 103, the upper bearing 104, the lower bearing 105, the vane 106, and the suction hole 107a. The drive shaft 101 has an eccentric shaft 101a. The piston 102 is fitted to the eccentric shaft 101a. The cylinder 103 accommodates the piston 102, which rotates eccentrically. The upper bearing 104 and the lower bearing 105 close the upper and lower opening faces of the cylinder 103. The vane 106 divides the space formed by the cylinder 103, the piston 102, the upper bearing 104, and the lower bearing 105 into a suction chamber 112 and a compression chamber 113, and moves integrally with the piston 102. The suction hole 107a is provided in the upper bearing 104 rather than in the cylinder 103, and is connected to a suction liner 114 and an accumulator 115. The suction liner 114 and accumulator 115 introduce suction gas from outside the rotary compressor 100 into the suction chamber 112 .

This eliminates the need for a spring on the back of the vane 106, which was necessary in conventional rolling piston type compressors, and allows the inner diameter D of the cylinder 103 to be increased and the height H to be reduced accordingly. This reduces the cross-sectional area of the leakage gap at the contact seal between the outer periphery of the piston 102 and the inner periphery of the cylinder 103, reducing leakage loss from the compression chamber 113 to the suction chamber 112. At the same time, a sufficiently large diameter suction hole 107a can be provided to ensure the cross-sectional area of the suction passage 107. Therefore, when a small diameter suction hole 107a is provided in a cylinder 103 with a low height H, pressure loss occurs in the suction passage 107, but this does not increase the pressure loss, and the compressor efficiency can be improved.

In addition, the rotary compressor 100 of this embodiment uses carbon dioxide as the working fluid.

Compared to other refrigerants such as HFC-based refrigerants, HC-based refrigerants, or HFO-based refrigerants, this carbon dioxide refrigerant has a large pressure difference between the suction chamber 112 and the compression chamber 113. Therefore, leakage loss at the seal portion between the piston 102 and the cylinder 103 has a large impact on the compressor efficiency. However, with the configuration disclosed herein, the height H of the cylinder 103 can be set extremely low, so the area of the seal portion between the piston 102 and the cylinder 103 can be reduced. Therefore, leakage loss can be more effectively reduced to improve compressor efficiency.

In addition, the rotary compressor 100 of this embodiment has a ratio D/H of the inner diameter D to the height H of the cylinder 103 in the range of 2 to 13.

This makes it possible to avoid the above-mentioned effects being reduced when D/H is too small, or the surface areas of the suction chamber 112 and compression chamber 113 increasing and the heat loss increasing when D/H is too large. This makes it possible to maximize the compressor efficiency.

It is more preferable to keep the above D/H in the range of 2 to 8.

This makes it possible to avoid the distance between the axis of the drive shaft 101 and the axis of the eccentric shaft 101a, i.e., the amount of eccentricity, becoming extremely large, which would result in a deterioration in the insertability of the piston 102. As a result, it is possible to realize a rotary compressor 100 that is easy to assemble and highly efficient.

In addition, in the rotary compressor 100 of this embodiment, an engagement groove 102a is formed in the piston 102, and an engagement portion 106a is provided on the tip side of the vane 106. This engagement portion 106a is fitted into the engagement groove 102a of the piston 102, thereby connecting the engagement portion 106a so that it can swing freely.

This eliminates the need for major design changes to the piston 102 and does not increase the number of parts. This keeps costs to a minimum.

The rotary compressor 100 of this embodiment is used in a refrigeration cycle device. Since the piston 102 and the vane 106 are connected in the configuration described above, vane jumping, which is an issue with conventional rolling piston types, does not occur, and low noise and high efficiency can be achieved. Therefore, operation is possible even under operating conditions such as low compression ratios. The expanded operating range of the rotary compressor 100 improves the freedom of operation of the refrigeration cycle device and improves system efficiency.

In addition, the rotary compressor 100 of this embodiment is used in a heat pump water heater.

The temperature of the discharge gas of a heat pump water heater is higher than that of other refrigeration cycle devices. Therefore, the temperature of the lower bearing 105 exposed to the high-temperature discharge gas also becomes high, and the impact of the decrease in volumetric efficiency due to the heat reception of the low-temperature intake gas passing through the intake passage 107 is large. However, in the rotary compressor of the present disclosure, the inner diameter D of the cylinder 103 is large, in other words, the distance from the inner wall of the sealed container 108 to the inner wall of the cylinder 103 is short, so the length of the intake passage 107 is also short. Therefore, the intake gas is less likely to receive heat, and the volumetric efficiency can be improved more effectively.

(Embodiment 2)
The second embodiment will be described below with reference to FIG.

[2-1. Configuration]
The rotary compressor 200 according to the second embodiment is configured with two cylinders, an upper cylinder 2031 and a lower cylinder 2032, and a partition plate 221 is provided between the upper cylinder 2031 and the lower cylinder 2032. This point differs from the rotary compressor 100 according to the first embodiment, which is configured with one cylinder 103.

The upper cylinder 2031, upper piston 2021 and upper vane (not shown) are sandwiched between the upper bearing 204 and the partition plate 221, the lower cylinder 2032, lower piston 2022 and lower vane (not shown) are sandwiched between the partition plate 221 and the lower bearing 205, and the space formed between the upper and lower cylinders 2031, 2032 and the upper and lower pistons 2021, 2022 is divided by the upper and lower vanes. In this way, an upper suction chamber 2121, a lower suction chamber 2122 (not numbered), an upper compression chamber 2131 (not numbered) and a lower compression chamber 2132 are formed, and each compression element is configured to perform a compression operation.

An upper suction passage 2071 is provided in the upper bearing 204. The upper suction passage 2071 is composed of a radial upper suction hole 2071a and an axial upper vertical hole 2071b, and communicates with the upper suction chamber 2121. A lower suction passage 2072 is provided in the lower bearing 205. The lower suction passage 2072 is composed of a radial lower suction hole 2072a and an axial lower vertical hole 2072b, and communicates with the lower suction chamber 2122.

The trapped volume of the rotary compressor 200 is the same as that of the rotary compressor 100 in embodiment 1, but since it is shared by two cylinders 2031 and 2032, the heights Hu and Hl of the cylinders 2031 and 2032 are lower than the height H of the cylinder 103 of the rotary compressor 100 in embodiment 1.

[2-2. Operation]
The operation of the rotary compressor 200 configured as above will be described below.

[2-2-1. Inhalation Operation]
The intake gas separated into gas and liquid in the accumulator 215 branches into two pipes and is sucked into upper and lower suction chambers 2121 and 2122 through upper and lower suction passages 2071 and 2072.

[2-2-2. Compression Operation]
The compression operation of each compression element of the rotary compressor 200 is similar to that of the rotary compressor 100 according to the first embodiment. However, the upper and lower compression chambers 2131 and 2132 perform compression in opposite phases.

The lower discharge gas compressed in the lower cylinder 2032 flows through a communication passage (not shown) into the muffler chamber 217 and merges with the upper discharge gas compressed in the upper cylinder 2031. The subsequent flow of the discharge gas is the same as that of the rotary compressor 100 according to the first embodiment.

[2-3. Effects, etc.]
As described above, in this embodiment, the rotary compressor 200 includes the drive shaft 201, the upper piston 2021, the lower piston 2022, the upper cylinder 2031, the lower cylinder 2032, the upper bearing 204, the lower bearing 205, the upper and lower vanes, the upper suction hole 2071a, the lower suction hole 2072a, and the partition plate 221. The upper and lower compression elements are configured in the axial direction. The partition plate 221 is provided between the upper and lower compression elements. The upper bearing 204 and the lower bearing 205 support the drive shaft 201. The upper suction hole 2071a is provided in the upper bearing 204, and the lower suction hole 2072a is provided in the lower bearing 205.

As a result, by performing compression by the upper and lower pistons 2021, 2022 in opposite phases, torque fluctuations can be reduced and vibrations can be reduced compared to the rotary compressor 100 according to the first embodiment. In addition, the inner diameter D of the upper cylinder 2031 and the lower cylinder 203 can be increased and the heights Hu and Hl can be decreased, so that the leakage gap cross-sectional area of the contact seal portion between the outer periphery of the pistons 2021, 2022 and the inner periphery of the cylinders 2031, 2032 is further reduced, and leakage losses from the compression chambers 2131, 2132 to the suction chambers 2121, 2122 can be reduced. In addition, by providing the upper suction hole 2071a and the lower suction hole 2072a in the upper bearing 204 and the lower bearing 205, the diameters of the suction holes 2071a, 2072a can be made sufficiently large, and the cross-sectional area of the suction passages 2071, 2072 can be sufficiently secured. Therefore, when small-diameter suction holes 2071a, 2072a are provided in cylinders 2031, 2032 with low heights Hu, Hl, pressure loss occurs in the suction passages 2071, 2072, but there is no increase in pressure loss, and the compressor efficiency can be further improved.

(Embodiment 3)
The second embodiment will be described below with reference to FIG.

[3-1. Configuration]
The rotary compressor 300 according to the third embodiment differs from the rotary compressor 200 according to the second embodiment at least in that a suction hole 307 a is provided in a partition plate 321 instead of in an upper bearing 304 and a lower bearing 305 .

The partition plate 321 is provided with an intake passage 307 consisting of a radial intake hole 307a, an upper vertical hole 307b communicating with the upper intake chamber 3121, and a lower vertical hole 307c communicating with the lower intake chamber 3122 (not numbered).

[3-2. Operation]
The operation of the rotary compressor 300 configured as above will be described below.

[3-2-1. Inhalation Operation]
The intake gas separated into gas and liquid in the accumulator 315 is distributed to the upper and lower parts in the intake passage 307 and is then drawn into the upper and lower intake chambers 3121 and 3122 .

[3-2-2. Compression Operation]
The gas sucked into the upper and lower suction chambers 3121 and 3122 is compressed in the same manner as in the second embodiment.

[3-3. Effects, etc.]
As described above, in this embodiment, the rotary compressor 300 includes the drive shaft 301, the upper piston 3021, the lower piston 3022, the upper cylinder 3031, the lower cylinder 3032, the upper bearing 304, the lower bearing 305, the upper and lower vanes, the suction hole 307a, and the partition plate 321. The upper and lower compression elements are configured in the axial direction. The partition plate 321 is provided between the upper and lower compression elements. The upper bearing 304 and the lower bearing 305 support the drive shaft 301. The suction hole 307a is provided in the partition plate 321.

This allows the accumulator 115 of the rotary compressor 100 configured with one cylinder 103 according to the first embodiment to be used as is. Therefore, compared to the rotary compressor 200 according to the second embodiment, the number of parts and the number of assembly steps can be reduced, and a low-cost accumulator 315 and rotary compressor 300 can be realized. Other effects are the same as those of the second embodiment.

Other Embodiments
As described above, the first to third embodiments have been described as examples of the technology disclosed in this application. However, the technology in this disclosure is not limited to these, and can be applied to embodiments in which modifications, substitutions, additions, omissions, etc. are made. In addition, it is also possible to combine the components described in the first to third embodiments to create new embodiments.

Therefore, other embodiments are given below as examples.

In the first to third embodiments, the one-cylinder rotary compressor 100 and the two-cylinder rotary compressors 200 and 300 have been described as examples of rotary compressors. Any rotary compressor may be used as long as it compresses gas. Therefore, the rotary compressor is not limited to the one-cylinder rotary compressor 100 or the two-cylinder rotary compressors 200 and 300. However, the use of the one-cylinder rotary compressor 100 or the two-cylinder rotary compressors 200 and 300 has the advantage of being easy to mass-produce, with a good balance between cost, efficiency, and reliability. A two-stage compressor may also be used as the rotary compressor. If a two-stage compressor is used as the rotary compressor, the high-low pressure difference can be reduced even under operating conditions with a high pressure ratio, so high efficiency can be achieved with little leakage loss. The rotary compressor may also be provided with multiple vanes and compression chambers in one cylinder. By using this, in the configuration of the one-cylinder rotary compressor 100, torque fluctuations can be reduced by performing compression operations similar to those of the two-cylinder type, or the high-low pressure difference can be reduced by adopting a two-stage compression configuration. Therefore, a rotary compressor that can operate with low vibration or a high pressure ratio with a small number of parts can be realized.

In addition, in the first embodiment, the vane 106 having the engagement portion 106a that is oscillatably fitted and connected to the engagement groove 102a formed in the piston 102 has been described as an example of the vane. The vane may be any vane that divides the suction chamber and the compression chamber, always moves integrally with the piston, and does not require a spring on the back of the vane. Therefore, the vane is not limited to the vane 106 having the engagement portion 106a that is oscillatably fitted and connected to the engagement groove 102a formed in the piston 102. However, if this is used, as described above, there is no need to make major design changes to the piston 102, and the number of parts does not increase, so that the increase in cost can be minimized. In addition, if a swing type vane is used that is completely integrated with the piston and the piston oscillates through a swing bush provided in the cylinder, there is no contact point between the vane and the piston. Therefore, there is no leakage loss or sliding loss in the minute gap, and the rotary compressor 100 can be made highly efficient.

Furthermore, in the first embodiment, carbon dioxide has been described as an example of the working fluid. The working fluid may be any compressible fluid. Therefore, the working fluid is not limited to carbon dioxide. However, when this working fluid is used, the pressure difference between the suction chamber 112 and the compression chamber 113 is large compared to other refrigerants such as HFC refrigerants, HC refrigerants, or HFO refrigerants as described above, and the leakage loss at the seal portion between the piston 102 and the cylinder 103 has a large effect on the compressor efficiency. However, by using the configuration of the present disclosure to set the height H of the cylinder 103 extremely low, the leakage loss can be reduced more effectively. In addition, if a mixture of carbon dioxide and other refrigerants such as HFC refrigerants, HC refrigerants, or HFO refrigerants is used as the working fluid, the temperature glide between the condenser inlet and outlet of the refrigeration cycle can be suppressed. Therefore, the decrease in the heat exchange efficiency of the condenser can be suppressed.

Note that the above-described embodiments are intended to illustrate the technology disclosed herein, and various modifications, substitutions, additions, omissions, etc. may be made within the scope of the claims or their equivalents.

This disclosure is applicable to rotary compressors and refrigeration cycle devices in which leakage loss and pressure loss occur. Specifically, this disclosure is applicable to air conditioners, refrigerators, blowers, water heaters, etc.

100 Rotary compressor 101, 201, 301 Drive shaft 101a Eccentric shaft 102 Piston 102a Engagement groove 103 Cylinder 104, 204, 304 Upper bearing (upper end plate)
105, 205, 305 Lower bearing (lower end plate)
106 vane 106a engagement portion 107 suction passage 107a suction hole 107b vertical hole 108 sealed container 109 discharge pipe 110 electric motor 110a rotor 110b stator 111 compression mechanism 112 suction chamber 113 compression chamber 114 suction liner (suction piping)
115 Accumulator (suction piping)
116 Suction outer pipe (suction piping)
Reference Signs List 117 muffler chamber 118 muffler 119 space below motor 120 space above motor 200 rotary compressor 2021 upper piston 2022 lower piston 2031 upper cylinder 2032 lower cylinder 2071 upper suction passage 2071a upper suction hole 2071b upper vertical hole 2072 lower suction passage 2072a lower suction hole 2072b lower vertical hole 2121 upper suction chamber 2122 lower suction chamber 2131 upper compression chamber 2132 lower compression chamber 215 accumulator 217 muffler chamber 221 partition plate 300 rotary compressor 3021 upper piston 3022 lower piston 3031 upper cylinder 3032 lower cylinder 307 suction passage 307a Suction hole 307b Upper vertical hole 307c Lower vertical hole 3121 Upper suction chamber 3122 Lower suction chamber 315 Accumulator 321 Partition plate

Claims (7)

A drive shaft having an eccentric shaft;
a piston fitted to the eccentric shaft;
a cylinder that accommodates the piston that rotates eccentrically;
An upper end plate and a lower end plate that close the upper and lower opening surfaces of the cylinder;
a vane that divides a space defined by the cylinder, the piston, the upper end plate, and the lower end plate into a suction chamber and a compression chamber and moves integrally with the piston;
a suction passage provided in at least one of the upper end plate and the lower end plate for introducing suction gas from outside the compressor into the suction chamber;
Equipped with
a suction passage including a suction hole connected to a suction pipe and a vertical hole directly communicating in whole or in part with the suction chamber; a plurality of compression elements each including the cylinder, the piston, and the vane are provided in an axial direction;
A partition plate is provided between the plurality of compression elements.
The rotary compressor according to claim 1 . Using carbon dioxide as the working fluid,
The rotary compressor according to claim 1 or 2. The ratio D/H of the inner diameter D to the height H of the cylinder is in the range of 2 to 13;
The rotary compressor according to any one of claims 1 to 3. An engagement groove formed in the piston;
an engagement portion provided on a tip side of the vane and pivotably fitted and connected to the engagement groove;
The rotary compressor according to any one of claims 1 to 4. A refrigeration cycle device equipped with a rotary compressor according to any one of claims 1 to 5. It is a heat pump water heater.
The refrigeration cycle device according to claim 6.