RU2535307C2 - Rotary piston compressor - Google Patents

Rotary piston compressor Download PDF

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Publication number
RU2535307C2
RU2535307C2 RU2013106968/06A RU2013106968A RU2535307C2 RU 2535307 C2 RU2535307 C2 RU 2535307C2 RU 2013106968/06 A RU2013106968/06 A RU 2013106968/06A RU 2013106968 A RU2013106968 A RU 2013106968A RU 2535307 C2 RU2535307 C2 RU 2535307C2
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RU
Russia
Prior art keywords
crankcase
cover
ejector
lubricant
compressor
Prior art date
Application number
RU2013106968/06A
Other languages
Russian (ru)
Other versions
RU2013106968A (en
Inventor
Максим Викторович Оленич
Борис Георгиевич Нехорошев
Original Assignee
Максим Викторович Оленич
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to UAa201009470A priority Critical patent/UA104999C2/en
Priority to UAa201009470 priority
Application filed by Максим Викторович Оленич filed Critical Максим Викторович Оленич
Priority to PCT/UA2011/000059 priority patent/WO2012023916A1/en
Publication of RU2013106968A publication Critical patent/RU2013106968A/en
Application granted granted Critical
Publication of RU2535307C2 publication Critical patent/RU2535307C2/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02Lubrication; Lubricant separation
    • F04C29/028Means for improving or restricting lubricant flow
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02Lubrication; Lubricant separation
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/04Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of internal-axis type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06Silencing
    • F04C29/068Silencing the silencing means being arranged inside the pump housing
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/22Rotary-piston pumps specially adapted for elastic fluids of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth equivalents than the outer member

Abstract

FIELD: engines and pumps.
SUBSTANCE: invention can be used in stationary and mobile gas and refrigeration plants, air conditioner and heat pumps. Rotary piston compressor comprises epitrochoidal housing 1 and rotor 5 fitted on a camshaft, crankcase to keep lubricant secured to rear side cover. Ejector is arranged inside said crankcase. System of channels is composed of radial or inclined bore 14 in housing 1 in expansion zone and communicated therewith via larger diameter chamber of axial bore 15 communicated with said ejector. Side cover working surfaces have radial channels 23 for communication via circular clearance between the shaft and rear cover, crankcase cavity with working chambers 8, 9 at suction stroke. Lubricant dispenser is composed of spring-loaded valve and resilient split ring with preset metering clearance at the point of split. Said valve is arranged ahead of ejector in larger diameter chamber. Split ring is fitted in circular clearance between shaft and rear cover. Note here that said clearance is shut off by said ring.
EFFECT: efficient batched feed of lubricant to compressor friction parts.
5 cl, 6 dwg

Description

The invention relates to the field of compressor engineering and can be used in stationary and transport gas (air) and refrigeration units, air conditioners and heat pumps.

The advantages of rotary piston compressors over reciprocating compressors are the absence of elements with reciprocating motion, which allows to provide good specific indicators in terms of mass and dimensions, reducing the level of vibration and noise.

Known rotary piston compressor containing an epitrochoidal housing with front and rear side covers and a rotor located in its cavity located on an eccentric shaft, while the housing, side covers and rotor form working chambers of variable volume, a lubrication system of compressor working surfaces containing an oil tank for lubricant content, a lubricant spraying device in the form of an ejector, the nozzle of which is communicated by a tube with the mentioned oil tank, and a system of channels made in an eccentric shaft and connecting the ejector to working chambers (AS USSR No. 315800, publ. 01.10.1971, bull. No. 29).

The specificity of rotary piston compressors is that, due to the lack of space for efficient rotor mechanical seals and the difficulty of removing oil from it, the simplest and most reliable way to prevent its excessive quantity entering the working chambers is to dispense its supply.

The disadvantages of the known rotary piston compressor:

1. No dosing of the amount of oil supplied.

2. Since the ejector is constantly connected to the working chambers and the oil tank, an excess, uncontrolled amount of oil is sucked in through it during suction, which, due to the previously noted specificity of rotary piston compressors, is for the most part discharged into gas (air) rotary piston compressors into the atmosphere, worsening ecology, increasing the loss of oil from the system, leads to increased carbon formation, especially in the discharge valve.

3. Additionally, an oil tank is required that is not structurally included in the compressor located outside it, as well as an ejector with oil lines. At low ambient temperatures, which reach up to minus 55 ° С under operating conditions, the oil thickens so much that without its forced heating in the oil tank by an external heat source, the ejector (and, perhaps, of a different type of pump) cannot suck it from the oil tank and give it to the consumer .

4. The ejector works only in the presence of a certain pressure drop, while in operation it can be (significantly) lower, for example, when performing sandblasting, painting and other work, in which the ejector does not work.

5. The ejector is made of pipes of small outer diameter - about 8 ... 10 mm, and since they are located outside the compressor, they can easily be damaged (broken) during transportation and operation of the compressor.

6. Installing an ejector in front of the front end of the shaft eliminates (or greatly complicates) the possibility of installing an impeller for the impeller on it.

Also known is a rotary piston compressor containing an epitrochoid housing with front and rear side covers and a rotor located in its cavity located on an eccentric shaft, while the housing, side covers and rotor form working chambers of variable volume, a lubrication system for compressor working surfaces having a crankcase for the content of lubricant, a device for spraying lubricant in the form of an ejector, the nozzle of which is communicated by a tube with the bottom of the crankcase, a system of channels connecting the ejector to working chambers, and a device for zirovaniya supplying lubricant into the axial bore of the eccentric shaft (AS USSR №1231263, publ. 15.05.1986, Bul. №18, prototype).

This compressor partially eliminated the first of the above disadvantages, namely, at the inlet to the radial drilling of the eccentric shaft, a dispenser is installed in the form of a rotary damper with an actuator equipped with a time relay, which reduces the amount of gas-oil mixture supplied to the shaft during the expansion process.

However, this dispenser complicates the design and reduces the reliability of the compressor.

In addition, it has the remaining disadvantages listed above.

The basis of the invention is the task of creating a rotary piston compressor, in which by changing the location of the ejector and switching the channels of the lubrication system, as well as introducing new structural elements, an economical metered supply of lubricant to the rubbing surfaces of the compressor is provided.

The problem is solved in that in a rotary piston compressor containing an epitrochoid housing with front and rear side covers and a rotor located in its cavity located on an eccentric shaft, the housing, side covers and rotor form working chambers of variable volume, a lubrication system for workers compressor surfaces having a crankcase for containing grease, a lubricant spraying device in the form of an ejector, the nozzle of which is communicated by a tube with the bottom of the crankcase, a system of channels connecting the ejector to the working Here, the device for dispensing the lubricant supply, according to the invention, the channel system is implemented in the form of a radial or inclined hole made in the housing in the expansion zone and connected to it through a larger diameter chamber, passing axially through the housing, the flange of the rear side cover and the front flange of the crankcase, and connected to the ejector, and on the working surfaces of the side covers are made radial channels for connection through an annular gap formed between the eccentric shaft and the rear a new cover, the crankcase cavities with working chambers during the suction period, and the lubricant metering device is made in the form of a spring-loaded valve and a split elastic ring, mainly made of antifriction material, having a gap of a predetermined metering value at the section of the cut, of which the spring-loaded valve is installed in front of the ejector in the said chamber of larger diameter, and a split ring is installed in the annular gap between the eccentric shaft and the rear side cover, and this ring is closed by an elastic ring evi gap and formed in the place of its cut the gap of a given dosing value.

A buffer volume is made above the spring-loaded valve.

The split ring can be installed both in the annular groove made in the hole of the rear side cover and in the annular groove made in the body of the eccentric shaft.

An additional lubricant spraying device is installed in the crankcase, made in the form of a driven gear and a driven gear, the pinion gear is rigidly fixed to the eccentric shaft, and the axis of the driven gear is fixedly mounted in the lower part of the rear side cover so that part of this gear is located lower lower lubrication mark.

The implementation of the compressor in accordance with the proposed invention provides the following advantages:

The proposed compressor provides more accurate dosing of the amount supplied to the rubbing parts of the working chambers of oil.

During suction, the necessary and controlled amount of oil is sucked in. Therefore, its emission into the atmosphere is reduced to a minimum, and carbon formation is reduced. There is no need for an oil tank, because the crankcase is structurally included in the compressor. At low ambient temperatures, oil is heated from the rear side cover of the compressor. Despite the fact that the ejector works only in the presence of a certain pressure drop, and in operation it can be (significantly) lower, for example, when performing sandblasting, painting and other works, in which the ejector does not work, however, the lubrication system also works , since the oil is sprayed with an additional, duplicating system, consisting of two rotating gears meshed, the lower of which - driven - is constantly located in the oil pan of the crankcase.

Since the ejector is placed in the crankcase, the possibility of damage to its tubes during transportation and operation of the compressor is excluded.

The invention is illustrated by drawings, in which:

figure 1 is a longitudinal section of a compressor,

figure 2 is a transverse view of the compressor with the front cover removed,

figure 3 and figure 4 - fragments of the lubrication system,

figure 5 and figure 6 - options for the location of the metering rings.

The rotary piston compressor (hereinafter referred to as the compressor) consists of an epitrochoid casing 1, closed from the ends of the front 2 and rear 3 side

covers, an eccentric shaft 4, on the eccentric part of which a rotor 5 is mounted. A crankcase 6 is attached to the end of the rear side cover 3, closed from the rear end by the crankcase cover 7. The lower part of the crankcase is filled with oil (Fig. 1), there is no breather in the crankcase.

The epitrochoid casing 1, side covers 2, 3 and rotor 5 form working chambers 8 and 9 of variable volume. In Fig.2, the rotor 5 is depicted in two positions: a solid line when the volume of the chamber 8 is minimal (harmful), the chamber 9 is the maximum (full), and the dotted line is in the intermediate position when the inlet window 10 begins to open.

The discharge valve 11 is installed in the outlet (discharge) well of the housing 1. In the rotor 5, radial 12 and end 13 sealing strips are installed, which are pressed to the working surfaces by expanders and provide sealing of the working chambers 8 and 9.

The lubrication system (FIGS. 2, 3 and 4) of the compressor is implemented as an inclined or radial hole 14 made in the working surface of the epitrochoidal housing 1 in the zone of the expansion process and the axial hole 15 connected to it, passing through the epitrochoidal housing 1, the rear side flange the cover 3 and the front flange of the crankcase 6, to which the ejector is coaxially connected, consisting of a nozzle 16 and a tube 17 (Figs. 1, 3, 4), while the radial 14 or axial 15 holes in the epitrochoid housing are made coaxially or perpendicularly connected to it cylindrical chamber 18 is greater than the suitable holes 14 and 15 diameter, with a closed end at the axial location of the front side chamber cover 2 (Figure 3) at a radial location - a plug 19 (Figure 4). A self-acting valve 20 is installed in the cylindrical chamber 18 in the form of a piston (Figs. 3, 4) or a ball, not shown in the figures. An additional buffer volume 21 is attached to the cylindrical chamber 18, and a spring 22 is mounted above the piston (ball); on the working surfaces of the side covers 2 and 3, radial channels 23 are made (FIG. 2), connecting the crankcase cavity 6 with the working chambers 8 and 9 through the annular gap between the eccentric shaft 4 and the rear side cover 3 during the suction process.

Placing the ejector inside the crankcase 6 near the rear side cover 3 improves its working conditions at low temperatures, since during operation of the compressor, the cover 3 heats up, heating and oil located near it, reducing its viscosity. The ejector inside the crankcase is protected against breakage. At the passage of the eccentric shaft 4 in the hole of the rear side cover 3, annular grooves are made in it or in the eccentric shaft for installation mainly of anti-friction material of split rings 24 (Fig. 5) or 25 (Fig. 6), which they are pressed against the eccentric shaft 4 (Fig. 5) or to the hole of the rear side cover 3 (Fig. 6) by the force of their own elasticity and have a predetermined gap at the point of the cut, which doses the amount of gas oil mixture.

The compressor further comprises, inside the crankcase, a drive gear 26 rigidly fixed to the eccentric shaft 4 and a driven gear 27 (FIG. 1), which is constantly engaged with it, mounted on an axis 28, which is fixedly mounted in the tide of the lower part of the rear side cover 3 so that the lower part of the driven gear was constantly in the oil, regardless of its level. The specified gear pair is an additional duplicate means of spraying lubricant.

The compressor operates as follows. The eccentric shaft 4 is driven in rotation from the motor shaft (not shown conditionally). From the eccentric shaft, rotation is transmitted to the rotor 5, which performs a planetary motion, rotating with the shaft and turning relative to it. When the rotor rotates, the volume of the working chambers 8 and 9 cyclically changes from minimum to maximum, due to which the working process is carried out. 1 and 2, the solid lines of the rotor 5 are shown in the initial position, when the pumping process has ended in the working chamber 8, the suction process has ended in the working chamber 9, inertial replenishment is ongoing. 2, the rotor 5 is shown in dashed lines in an intermediate position when the expansion process has ended (or is close to the end) in the working chamber 8 and the inlet window 10 begins to open with the radial bar 12, starting the suction process. Gas is sucked in through the inlet window 10. A compression process takes place in the working chamber 9, when the discharge pressure is reached, the discharge valve 11 opens and the compressed gas is pushed out of it. After the arrival of the rotor 5 to its original position, the working chambers 8 and 9 are interchanged, then the cycle repeats.

The compressor is lubricated with a gas-oil mixture. When the radial sealing strip 12 passes the radial hole 14 (Figs. 3, 4), the gas having a high pressure is pushed into it, presses the spring 22 and, as shown in Figs. 3 and 4, moves the piston (ball) 20 to the leftmost position (Fig. 3) or the highest position (Fig. 4), opening the gas flow to the axial hole 15, the ejector nozzle 16 and creating a vacuum in its smaller cross-sectional area, due to which oil is sucked from the crankcase 6 through the tube 17 and expelled nozzle 16 into the crankcase in the form of finely dispersed gas oil Mesi filling the crankcase. Since the working chambers 8 and 9 are connected to the crankcase through the annular gap between the rear side cover 3 and the eccentric shaft 4, as well as the radial channels 23, the gas-oil mixture is sucked into them during the suction process. For dosing the amount of gas-oil mixture supplied to the lubricant in the annular gap, elastic split rings 24 or 25 are installed in the rear side cover 3 (Fig. 5) or in the eccentric shaft 4 (Fig. 6), having a clearance of a given (dosing) value Ho with working chambers 8 and 9, during the suction process, an ejector nozzle 16 is connected, through which the gas-oil mixture can be sucked into the working chambers. In order to block its entry or limit it to the necessary amount for lubricating the working surface of the epitrochoid body 1, a piston (ball) 20 is installed, which, under the influence of rarefaction in the working chambers 8 or 9 and the efforts of the spring 22, sit on their seats, completely or partially blocking the passage for suction of gas oil mixtures. Thus, it is possible to avoid increased oil consumption, carbonization, emission into the atmosphere, environmental improvement. The lack of a breather also contributes to this. Additional buffer volume 21 weakens the effect of pumping strokes and facilitates the movement of the piston (ball) 20.

To ensure reliable, trouble-free operation of the compressor, a duplicate lubrication system is also used. With a high oil viscosity and compressor operation at reduced conditions, when the gas pressure during expansion is insufficient and the ejector cannot work, the oil in the crankcase 6 will be sprayed by the driven gear 27 immersed in it, driven by the drive gear 26.

Claims (5)

1. A rotary piston compressor comprising an epitrochoid casing with front and rear side covers and a rotor located in its cavity located on an eccentric shaft, while the casing, side covers and rotor form working chambers of variable volume, a compressor working surface lubrication system having a crankcase for the content of lubricant, a device for spraying lubricant in the form of an ejector, the nozzle of which is communicated by a tube with the bottom of the crankcase, a system of channels connecting the ejector to the working chambers, and a device for dispensing according to A lubricant, characterized in that the crankcase for containing the lubricant is attached to the rear side cover, the ejector is installed inside the crankcase, and the channel system is made in the form of a radial or inclined hole made in the housing in the expansion zone and connected to it through a larger diameter axial hole passing through the housing, the flange of the rear side cover and the front flange of the crankcase, and connected to the ejector, radial channels are made on the working surfaces of the side covers for connection through an annular gap, made between the eccentric shaft and the rear side cover, the crankcase cavities with the working chambers during the suction period, while the lubricant dispensing device is made in the form of a spring-loaded valve and a split elastic ring, mainly made of antifriction material having a gap of a predetermined dispensing value at the section of the cut, from which a spring-loaded valve is installed in front of the ejector in the aforementioned chamber of a larger diameter, and a split elastic ring is installed in the annular gap between the eccentric shaft and the rear a side cover, and this annular gap is closed by a ring and a gap of a predetermined dosing quantity is formed in the place of its cut.
2. The rotary piston compressor according to claim 1, characterized in that a buffer volume is formed above the spring-loaded valve.
3. The rotary piston compressor according to claim 1, characterized in that the split elastic ring is installed in the annular groove made in the hole of the rear side cover.
4. The rotary piston compressor according to claim 1, characterized in that the split elastic ring is installed in an annular groove made in the body of the eccentric shaft.
5. The rotary piston compressor according to claim 1, characterized in that an additional backup lubricant spraying means is installed in the crankcase, made in the form of engaged and driven gears, while the drive gear is rigidly fixed to the eccentric shaft, and the axis of the driven gear is stationary fixed in the lower part of the rear side cover so that part of this gear is located below the lower lubrication mark.
RU2013106968/06A 2010-07-28 2011-07-26 Rotary piston compressor RU2535307C2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
UAa201009470A UA104999C2 (en) 2010-07-28 2010-07-28 Rotary piston compressor
UAa201009470 2010-07-28
PCT/UA2011/000059 WO2012023916A1 (en) 2010-07-28 2011-07-26 Rotary piston compressor

Publications (2)

Publication Number Publication Date
RU2013106968A RU2013106968A (en) 2014-09-10
RU2535307C2 true RU2535307C2 (en) 2014-12-10

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ID=56266868

Family Applications (1)

Application Number Title Priority Date Filing Date
RU2013106968/06A RU2535307C2 (en) 2010-07-28 2011-07-26 Rotary piston compressor

Country Status (6)

Country Link
EP (1) EP2647846A4 (en)
KR (1) KR20130092568A (en)
CN (2) CN203641013U (en)
RU (1) RU2535307C2 (en)
UA (1) UA104999C2 (en)
WO (1) WO2012023916A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2715767C2 (en) * 2019-04-18 2020-03-03 Борис Георгиевич Нехорошев Rotary piston compressor or vacuum pump

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2685045T3 (en) * 2013-12-18 2018-10-05 Carrier Corporation Improved viscosity of the refrigerant compressor lubricant
CN104454545B (en) * 2014-11-27 2016-07-06 西安交通大学 A kind of compressor fuel injector with air suction function
JP2020513082A (en) 2017-04-07 2020-04-30 スタックポール インターナショナル エンジニアード プロダクツ,リミテッド.Stackpole International Engineered Products, Ltd. Epitrochoid vacuum pump

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3322069A1 (en) * 1983-06-18 1984-12-20 Armatec Fts Armaturen Pressurised gas machine, especially a compressor, with circulating lubrication
SU1160112A1 (en) * 1984-01-06 1985-06-07 Хмельницкий Завод Тракторных Агрегатов Lubrication system for rotary piston compressor
SU1231263A1 (en) * 1984-11-27 1986-05-15 Харьковский Ордена Ленина Авиационный Институт Им.Н.Е.Жуковского Rotary-piston compressor
RU21301U1 (en) * 2000-12-21 2002-01-10 Романов Федор Федорович Rotary-veined internal combustion engine

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US1686569A (en) * 1925-11-19 1928-10-09 Standard Pump & Supply Company Compressor
JPS6151678B2 (en) * 1980-03-27 1986-11-10 Matsushita Electric Ind Co Ltd
DE69132867T2 (en) * 1990-08-01 2002-09-12 Matsushita Electric Ind Co Ltd Rotary lobe system for liquid media
JP2004092710A (en) * 2002-08-30 2004-03-25 Honda Motor Co Ltd Method for assembling gear device and oil lubricating structure for gear device

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3322069A1 (en) * 1983-06-18 1984-12-20 Armatec Fts Armaturen Pressurised gas machine, especially a compressor, with circulating lubrication
SU1160112A1 (en) * 1984-01-06 1985-06-07 Хмельницкий Завод Тракторных Агрегатов Lubrication system for rotary piston compressor
SU1231263A1 (en) * 1984-11-27 1986-05-15 Харьковский Ордена Ленина Авиационный Институт Им.Н.Е.Жуковского Rotary-piston compressor
RU21301U1 (en) * 2000-12-21 2002-01-10 Романов Федор Федорович Rotary-veined internal combustion engine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2715767C2 (en) * 2019-04-18 2020-03-03 Борис Георгиевич Нехорошев Rotary piston compressor or vacuum pump

Also Published As

Publication number Publication date
EP2647846A4 (en) 2015-02-25
UA104999C2 (en) 2014-04-10
EP2647846A1 (en) 2013-10-09
CN203321830U (en) 2013-12-04
KR20130092568A (en) 2013-08-20
RU2013106968A (en) 2014-09-10
CN203641013U (en) 2014-06-11
WO2012023916A1 (en) 2012-02-23

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