21 research outputs found
Method for Calculating the Static Characteristics of Radial Hydrostatic Compensator of Machine Tool Bearings Deformation
The design, mathematical model and methods of calculating static characteristics of the radial hydrostatic compensator of machine tool bearings deformation are considered. The research has shown that the design is able to provide a stable value of negative compliance in the range of small and moderate load values. It has been identified that the type of characteristics largely depends on the adjustment factor of the input choke hydraulic resistance, for which there is an optimal value in terms of the load characteristics stability. The example of calculating the compensatorβ²s parameters is given, and it is shown that the compensator is capable to provide the functions for the machine with real characteristics
Compliance of Gas-Dynamic Bearing with Elastic Compensator of Movement
ΠΡΠ΅Π΄ΡΡΠ°Π²Π»Π΅Π½Π° ΠΊΠΎΠ½ΡΡΡΡΠΊΡΠΈΡ, ΠΏΡΠΈΠ²Π΅Π΄Π΅Π½Ρ ΠΌΠ°ΡΠ΅ΠΌΠ°ΡΠΈΡΠ΅ΡΠΊΠ°Ρ ΠΌΠΎΠ΄Π΅Π»Ρ ΠΈ ΠΌΠ΅ΡΠΎΠ΄ΠΈΠΊΠ° ΡΠ°ΡΡΠ΅ΡΠ°
ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΠΈ Π³Π°Π·ΠΎΠ΄ΠΈΠ½Π°ΠΌΠΈΡΠ΅ΡΠΊΠΎΠ³ΠΎ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠ° Ρ ΡΠ»Π°ΡΡΠΈΡΠ½ΡΠΌ ΠΊΠΎΠΌΠΏΠ΅Π½ΡΠ°ΡΠΎΡΠΎΠΌ ΠΏΠ΅ΡΠ΅ΠΌΠ΅ΡΠ΅Π½ΠΈΡ.
ΠΠΎΠΊΠ°Π·Π°Π½ΠΎ, ΡΡΠΎ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊ ΠΌΠΎΠΆΠ΅Ρ ΠΎΠ±Π»Π°Π΄Π°ΡΡ ΡΠΊΠΎΠ»Ρ ΡΠ³ΠΎΠ΄Π½ΠΎ ΠΌΠ°Π»ΠΎΠΉ ΠΏΠΎΠ»ΠΎΠΆΠΈΡΠ΅Π»ΡΠ½ΠΎΠΉ, Π° ΡΠ°ΠΊΠΆΠ΅
Π½ΡΠ»Π΅Π²ΠΎΠΉ ΠΈ ΠΎΡΡΠΈΡΠ°ΡΠ΅Π»ΡΠ½ΠΎΠΉ ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΡΡThe design, the mathematical model and calculation method of compliance of a gas-dynamic
bearing with elastic compensator of movement presented. It is shown that the bearing can have
an arbitrarily small positive as well as negative and zero complianc
Characteristics of Radial Gas-Static Bearing of Step Type
Π Π°ΡΡΠΌΠΎΡΡΠ΅Π½Π° ΠΊΠΎΠ½ΡΡΡΡΠΊΡΠΈΡ ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½ΠΎΠ³ΠΎ Π³Π°Π·ΠΎΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΎΠ³ΠΎ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠ° ΡΡΡΠΏΠ΅Π½ΡΠ°ΡΠΎΠ³ΠΎ
ΡΠΈΠΏΠ°. Π ΡΡΠ°Π²Π½Π΅Π½ΠΈΠΈ Ρ ΡΡΠ°Π΄ΠΈΡΠΈΠΎΠ½Π½ΡΠΌΠΈ Π΄ΡΠΎΡΡΠ΅Π»ΡΠ½ΡΠΌΠΈ Π³Π°Π·ΠΎΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΈΠΌΠΈ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠ°ΠΌΠΈ
ΡΡΡΡΠΎΠΉΡΡΠ²ΠΎ ΠΎΡΠ»ΠΈΡΠ°Π΅ΡΡΡ ΠΏΡΠΎΡΡΠΎΡΠΎΠΉ ΠΊΠΎΠ½ΡΡΡΡΠΊΡΠΈΠΈ ΠΈ ΡΠ΅Ρ
Π½ΠΎΠ»ΠΎΠ³ΠΈΡΠ½ΠΎΡΡΡΡ. ΠΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊ Π²ΡΠ΅Π³Π΄Π°
ΡΡΡΠΎΠΉΡΠΈΠ². Π£ΠΌΠ΅Π½ΡΡΠ΅Π½ΠΈΠ΅ ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΠΈ Π½Π΅ΡΡΡΠ΅Π³ΠΎ ΡΠ»ΠΎΡ, ΠΊΠ°ΠΊ ΠΏΡΠ°Π²ΠΈΠ»ΠΎ, ΡΠΎΠΏΡΠΎΠ²ΠΎΠΆΠ΄Π°Π΅ΡΡΡ ΡΠΎΡΡΠΎΠΌ
Π±ΡΡΡΡΠΎΠ΄Π΅ΠΉΡΡΠ²ΠΈΡ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠ°. ΠΠ°Π²ΠΈΡΠΈΠΌΠΎΡΡΠΈ ΡΡΠ΅ΠΏΠ΅Π½ΠΈ ΡΡΡΠΎΠΉΡΠΈΠ²ΠΎΡΡΠΈ ΠΏΠΎ ΡΡΠ΄Ρ ΠΏΠ°ΡΠ°ΠΌΠ΅ΡΡΠΎΠ²
ΠΈΠΌΠ΅ΡΡ Π³Π»ΠΎΠ±Π°Π»ΡΠ½ΡΠΉ ΠΌΠ°ΠΊΡΠΈΠΌΡΠΌ, ΡΡΠΎ ΠΏΠΎΠ·Π²ΠΎΠ»ΡΠ΅Ρ, ΠΎΡΠ½ΠΎΠ²ΡΠ²Π°ΡΡΡ Π½Π° Π΄ΠΈΠ½Π°ΠΌΠΈΡΠ΅ΡΠΊΠΈΡ
ΡΠ°ΡΡΠ΅ΡΠ°Ρ
,
ΠΏΡΠΎΠ΅ΠΊΡΠΈΡΠΎΠ²Π°ΡΡ ΠΎΠΏΡΠΈΠΌΠ°Π»ΡΠ½ΡΠ΅ ΠΏΠΎ Π±ΡΡΡΡΠΎΠ΄Π΅ΠΉΡΡΠ²ΠΈΡ ΠΊΠΎΠ½ΡΡΡΡΠΊΡΠΈΠΈThe design of step gas-static bearing is considered. In comparison with conventional throttle gasstatic
bearings the device is characterized by simplicity of design and manufacturability. Bearing is
always stable. Decrease of compliance of the carrier gap is accompanied by increase of speed of the
bearing. Dependencies of degree of stability in a number of parameters have a global maximum, what
allows design optimal constructions based on dynamic calculation
Π§ΠΈΡΠ»Π΅Π½Π½ΠΎ-Π°Π½Π°Π»ΠΈΡΠΈΡΠ΅ΡΠΊΠΈΠΉ ΠΌΠ΅ΡΠΎΠ΄ ΠΎΠΏΡΠ΅Π΄Π΅Π»Π΅Π½ΠΈΡ ΡΡΠ°Π²Π½Π΅Π½ΠΈΠΉ ΡΠ²ΡΠ·ΠΈ Π»Π°ΠΏΠ»Π°ΡΠΎΠ²ΡΡ ΡΡΠ°Π½ΡΡΠΎΡΠΌΠ°Π½Ρ ΠΎΠ±ΠΎΠ±ΡΠ΅Π½Π½ΠΎΠ³ΠΎ ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½ΠΎΠ³ΠΎ Π±Π»ΠΎΠΊΠ° Π³Π°Π·ΠΎΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΈΡ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠΎΠ²
The paper proposes a numeric-analytical method for determining the communication equations
of Laplaceβs transformants of dynamic functions of the universal unit of radial externallypressurized
gas bearings which movable element makes small radial oscillations in the locality in
its central position. Method and obtained dependences provide links between integro-differential
Laplaceβs transformants of the unit such as load capacity and local input and output mass flow
rates with transformants of eccentricity and gas lubricant pressure at inlet and outlet of the
unit. It is shown that the local transfer functions of the unit model are rational functions of the
Laplaceβs transform variable and all such functions have a common denominator in the form of
a polynomial of this variable. The method allows to calculate the required dynamic criterion of
gas bearings containing this unit with prescribed accuracy. Founded dependences give ready
formulas for calculation dynamic criteria of radial single-row or multi-row ordinary passive or
active externally-pressurized gas bearings in which this unit can be used for description of radial
movement of its movable elementΠΡΠ΅Π΄Π»ΠΎΠΆΠ΅Π½ ΡΠΈΡΠ»Π΅Π½Π½ΠΎ-Π°Π½Π°Π»ΠΈΡΠΈΡΠ΅ΡΠΊΠΈΠΉ ΠΌΠ΅ΡΠΎΠ΄ ΠΎΠΏΡΠ΅Π΄Π΅Π»Π΅Π½ΠΈΡ Π»Π°ΠΏΠ»Π°ΡΠΎΠ²ΡΡ
ΡΡΠ°Π½ΡΡΠΎΡΠΌΠ°Π½Ρ
Π΄ΠΈΠ½Π°ΠΌΠΈΡΠ΅ΡΠΊΠΈΡ
ΡΡΠ½ΠΊΡΠΈΠΉ Π΄Π»Ρ ΡΠ½ΠΈΠ²Π΅ΡΡΠ°Π»ΡΠ½ΠΎΠ³ΠΎ ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½ΠΎΠ³ΠΎ Π±Π»ΠΎΠΊΠ° Π³Π°Π·ΠΎΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΈΡ
ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠΎΠ²,
ΠΏΠΎΠ΄Π²ΠΈΠΆΠ½ΡΠΉ ΡΠ»Π΅ΠΌΠ΅Π½Ρ ΠΊΠΎΡΠΎΡΠΎΠ³ΠΎ ΡΠΎΠ²Π΅ΡΡΠ°Π΅Ρ ΠΌΠ°Π»ΡΠ΅ ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½ΡΠ΅ ΠΊΠΎΠ»Π΅Π±Π°Π½ΠΈΡ Π² ΠΎΠΊΡΠ΅ΡΡΠ½ΠΎΡΡΠΈ Π΅Π³ΠΎ
ΡΠ΅Π½ΡΡΠ°Π»ΡΠ½ΠΎΠ³ΠΎ ΠΏΠΎΠ»ΠΎΠΆΠ΅Π½ΠΈΡ.
ΠΠ΅ΡΠΎΠ΄ ΠΈ ΠΏΠΎΠ»ΡΡΠ΅Π½Π½ΡΠ΅ Π·Π°Π²ΠΈΡΠΈΠΌΠΎΡΡΠΈ ΠΏΠΎΠ·Π²ΠΎΠ»ΡΡΡ ΡΡΡΠ°Π½ΠΎΠ²ΠΈΡΡ ΡΠ²ΡΠ·Ρ ΠΈΠ½ΡΠ΅Π³ΡΠΎ-Π΄ΠΈΡΡΠ΅ΡΠ΅Π½ΡΠΈΠ°Π»ΡΠ½ΡΡ
Π»Π°ΠΏΠ»Π°ΡΠΎΠ²ΡΡ
ΡΡΠ°Π½ΡΡΠΎΡΠΌΠ°Π½Ρ Π½Π΅ΡΡΡΠ΅ΠΉ ΡΠΏΠΎΡΠΎΠ±Π½ΠΎΡΡΠΈ ΠΈ Π»ΠΎΠΊΠ°Π»ΡΠ½ΡΡ
ΠΌΠ°ΡΡΠΎΠ²ΡΡ
ΡΠ°ΡΡ
ΠΎΠ΄ΠΎΠ² Π½Π° Π²Ρ
ΠΎΠ΄Π΅ ΠΈ
Π²ΡΡ
ΠΎΠ΄Π΅ Π±Π»ΠΎΠΊΠ° Ρ ΡΡΠ°Π½ΡΡΠΎΡΠΌΠ°Π½ΡΠ°ΠΌΠΈ ΡΠΊΡΡΠ΅Π½ΡΡΠΈΡΠΈΡΠ΅ΡΠ° ΠΈ Π΄Π°Π²Π»Π΅Π½ΠΈΠΉ ΡΠΌΠ°Π·ΡΠ²Π°ΡΡΠ΅Π³ΠΎ Π³Π°Π·Π° Π½Π° Π²Ρ
ΠΎΠ΄Π΅
ΠΈ Π²ΡΡ
ΠΎΠ΄Π΅ Π±Π»ΠΎΠΊΠ°. ΠΠΎΠΊΠ°Π·Π°Π½ΠΎ, ΡΡΠΎ Π»ΠΎΠΊΠ°Π»ΡΠ½ΡΠ΅ ΠΏΠ΅ΡΠ΅Π΄Π°ΡΠΎΡΠ½ΡΠ΅ ΡΡΠ½ΠΊΡΠΈΠΈ Π±Π»ΠΎΠΊΠ° ΠΏΡΠ΅Π΄ΡΡΠ°Π²Π»ΡΡΡ ΡΠΎΠ±ΠΎΠΉ
ΡΠ°ΡΠΈΠΎΠ½Π°Π»ΡΠ½ΡΠ΅ ΡΡΠ½ΠΊΡΠΈΠΈ ΠΏΠ΅ΡΠ΅ΠΌΠ΅Π½Π½ΠΎΠΉ ΠΏΡΠ΅ΠΎΠ±ΡΠ°Π·ΠΎΠ²Π°Π½ΠΈΡ ΠΠ°ΠΏΠ»Π°ΡΠ° ΠΈ ΡΡΠΎ Π²ΡΠ΅ ΡΠ°ΠΊΠΈΠ΅ ΡΡΠ½ΠΊΡΠΈΠΈ ΠΈΠΌΠ΅ΡΡ
ΠΎΠ±ΡΠΈΠΉ Π·Π½Π°ΠΌΠ΅Π½Π°ΡΠ΅Π»Ρ Π² Π²ΠΈΠ΄Π΅ ΠΏΠΎΠ»ΠΈΠ½ΠΎΠΌΠ° ΠΎΡΠ½ΠΎΡΠΈΡΠ΅Π»ΡΠ½ΠΎ ΡΡΠΎΠΉ ΠΏΠ΅ΡΠ΅ΠΌΠ΅Π½Π½ΠΎΠΉ.
ΠΠ΅ΡΠΎΠ΄ ΠΏΠΎΠ·Π²ΠΎΠ»ΡΠ΅Ρ Π²ΡΡΠΈΡΠ»ΡΡΡ ΡΡΠ΅Π±ΡΠ΅ΠΌΡΠΉ ΠΊΡΠΈΡΠ΅ΡΠΈΠΉ ΠΊΠ°ΡΠ΅ΡΡΠ²Π° Π΄ΠΈΠ½Π°ΠΌΠΈΠΊΠΈ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠΎΠ²,
ΡΠΎΠ΄Π΅ΡΠΆΠ°ΡΠΈΡ
Π΄Π°Π½Π½ΡΠΉ Π±Π»ΠΎΠΊ, Ρ Π½Π°ΠΏΠ΅ΡΠ΅Π΄ Π·Π°Π΄Π°Π½Π½ΠΎΠΉ ΡΠΎΡΠ½ΠΎΡΡΡΡ.
ΠΠ°ΠΉΠ΄Π΅Π½Π½ΡΠ΅ ΡΡΠ°Π²Π½Π΅Π½ΠΈΡ ΡΠ²ΡΠ·Π΅ΠΉ Π΄Π°ΡΡ Π³ΠΎΡΠΎΠ²ΡΠ΅ ΡΠΎΡΠΌΡΠ»Ρ Π΄Π»Ρ ΡΠ°ΡΡΠ΅ΡΠ° ΠΊΡΠΈΡΠ΅ΡΠΈΠ΅Π² ΠΊΠ°ΡΠ΅ΡΡΠ²Π°
Π΄ΠΈΠ½Π°ΠΌΠΈΠΊΠΈ ΡΠΎΠ΄Π΅ΡΠΆΠ°ΡΠΈΡ
ΡΠ°ΠΊΠΎΠΉ Π±Π»ΠΎΠΊ ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½ΡΡ
ΠΎΠ΄Π½ΠΎΡΡΠ΄Π½ΡΡ
, ΠΌΠ½ΠΎΠ³ΠΎΡΡΠ΄Π½ΡΡ
ΠΎΠ±ΡΡΠ½ΡΡ
ΠΏΠ°ΡΡΠΈΠ²Π½ΡΡ
ΠΈΠ»ΠΈ Π°ΠΊΡΠΈΠ²Π½ΡΡ
Π³Π°Π·ΠΎΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΈΡ
ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠΎΠ², Π² ΠΊΠΎΡΠΎΡΡΡ
ΡΠΎΠ²Π΅ΡΡΠ°Π΅ΡΡΡ ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½ΠΎΠ΅ Π΄Π²ΠΈΠΆΠ΅Π½ΠΈΠ΅
ΠΈΡ
ΠΏΠΎΠ΄Π²ΠΈΠΆΠ½ΡΡ
ΡΠ»Π΅ΠΌΠ΅Π½ΡΠΎ
Numerical Modeling on the Compliance and Load Capacity of a Two-Row Aerostatic Journal Bearing with Longitudinal Microgrooves in the Inter-Row Zone
Aerostatic bearings are attractive, with minimal friction losses, high durability, and environmental friendliness. However, such designs have a number of disadvantages, including low load-bearing capacity and high compliance due to high air compressibility and limited injection pressure. The article proposes a double-row aerostatic journal bearing with an external combined throttling system and longitudinal microgrooves in the inter-row zone. It is hypothesized that the use of microgrooves will reduce the circumferential flows of compressed air, as a result of which the compliance should decrease and the bearing capacity should increase. To test the hypothesis, we carried out the mathematical modeling, calculations, and theoretical study of stationary operation modes of the bearing for small shaft eccentricities in the vicinity of the central equilibrium position of the shaft and bearing capacity for arbitrary eccentricities. Formulas were obtained for the numerical evaluation of compliance for bearings with a smooth bushing surface and with longitudinal microgrooves. Iterative finite-difference methods for evaluating the fields of the squared pressure are proposed, on the basis of which the load capacity of the bearings is calculated. Experimental verification of the bearingβs theoretical characteristics was carried out, which showed satisfactory agreement between the compared data. The study of the compliance and load capacity of a microgroove bearing yielded impressive results. We show that the positive effect from the application of the improvement begins to manifest itself already at four microgrooves; the effect becomes significant at six microgrooves, and at twelve or more microgrooves, the circumferential flows in the bearing gap practically disappear; therefore, the bearing characteristics can be calculated on the basis of one-dimensional models of air lubrication longitudinal flow. Calculations have shown that for a length of L = 1, the maximum load capacity of a bearing with microgrooves is 1.5 times higher than that of a conventional bearing; for L β₯ 1.5, the bearing capacity increases twice or more. The result obtained allows us to recommend the proposed improvement for practical use in order to increase the load capacity of aerostatic journal bearings significantly
Static Characteristics of Active Hydrostatic Two-Row Radial Bearing with Restriction of Output Lubricant Flow
The design of active hydrostatic radial bearing with smooth cylindrical surfaces and lubricant output
flow restrictors in the form of movable rings on membrane suspension is presented.
The device is several times less power-consuming compared with known devices of flow control. The
bearing has a negative and zero compliance (infinite stiffness), and therefore can be used in machine
tools to suppress the negative influence of elastic system deformation on the accuracy of processing.
On the basis of two-dimensional model of lubricant flow developed a mathematical model, method
and procedure for calculating the bearing load capacity and flow rate. It is established, that the
calculation of static characteristics of bearing in the entire range of operating loads can be correctly
performed only on the base of two-dimensional model. For small eccentricities the characteristic of
zero and negative compliance can be calculated with sufficient accuracy by the simplified method,
based on one-dimensional motion of lubricant flow. Bearing of zero or negative compliance have
load capacity range, which is 20 - 50% more than conventional bearings of the same overall
dimensions. The setting of input throttling slits resistance decisive influence on the optimal static
characteristics of the bearing. The optimal values of its resistance for conventional and active
bearing are practically identical.Π Π°ΡΡΠΌΠΎΡΡΠ΅Π½Π° ΠΊΠΎΠ½ΡΡΡΡΠΊΡΠΈΡ Π°ΠΊΡΠΈΠ²Π½ΠΎΠ³ΠΎ Π³ΠΈΠ΄ΡΠΎΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΎΠ³ΠΎ ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½ΠΎΠ³ΠΎ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠ° Ρ Π³Π»Π°Π΄ΠΊΠΈΠΌΠΈ
ΡΠΈΠ»ΠΈΠ½Π΄ΡΠΈΡΠ΅ΡΠΊΠΈΠΌΠΈ ΡΠ°Π±ΠΎΡΠΈΠΌΠΈ ΠΏΠΎΠ²Π΅ΡΡ
Π½ΠΎΡΡΡΠΌΠΈ ΠΈ ΠΎΠ³ΡΠ°Π½ΠΈΡΠΈΡΠ΅Π»ΡΠΌΠΈ Π²ΡΡ
ΠΎΠ΄Π½ΠΎΠ³ΠΎ ΡΠΌΠ°Π·ΠΎΡΠ½ΠΎΠ³ΠΎ ΠΏΠΎΡΠΎΠΊΠ°
ΡΠΌΠ°Π·ΠΊΠΈ Π² Π²ΠΈΠ΄Π΅ ΠΏΠΎΠ΄Π²ΠΈΠΆΠ½ΡΡ
ΠΊΠΎΠ»Π΅Ρ Ρ ΠΌΠ΅ΠΌΠ±ΡΠ°Π½Π½ΡΠΌ ΠΏΠΎΠ΄Π²Π΅ΡΠΎΠΌ. Π£ΡΡΡΠΎΠΉΡΡΠ²ΠΎ Π² Π½Π΅ΡΠΊΠΎΠ»ΡΠΊΠΎ ΡΠ°Π· ΠΌΠ΅Π½Π΅Π΅
ΡΠ½Π΅ΡΠ³ΠΎΠ΅ΠΌΠΊΠΎ ΠΏΠΎ ΡΡΠ°Π²Π½Π΅Π½ΠΈΡ c ΠΈΠ·Π²Π΅ΡΡΠ½ΡΠΌΠΈ ΡΡΡΡΠΎΠΉΡΡΠ²Π°ΠΌΠΈ Ρ ΡΠ΅Π³ΡΠ»ΡΡΠΎΡΠ°ΠΌΠΈ ΡΠ°ΡΡ
ΠΎΠ΄Π°. ΠΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊ
ΠΎΠ±Π»Π°Π΄Π°Π΅Ρ ΠΎΡΡΠΈΡΠ°ΡΠ΅Π»ΡΠ½ΠΎΠΉ ΠΈ Π½ΡΠ»Π΅Π²ΠΎΠΉ ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΡΡ (Π±Π΅ΡΠΊΠΎΠ½Π΅ΡΠ½ΠΎΠΉ ΠΆΠ΅ΡΡΠΊΠΎΡΡΡΡ), ΠΏΠΎΡΡΠΎΠΌΡ
ΠΌΠΎΠΆΠ΅Ρ Π±ΡΡΡ ΠΈΡΠΏΠΎΠ»ΡΠ·ΠΎΠ²Π°Π½ Π² ΠΌΠ΅ΡΠ°Π»Π»ΠΎΡΠ΅ΠΆΡΡΠΈΡ
ΡΡΠ°Π½ΠΊΠ°Ρ
Π΄Π»Ρ ΠΏΠΎΠ΄Π°Π²Π»Π΅Π½ΠΈΡ Π½Π΅Π³Π°ΡΠΈΠ²Π½ΠΎΠ³ΠΎ Π²Π»ΠΈΡΠ½ΠΈΡ
Π΄Π΅ΡΠΎΡΠΌΠ°ΡΠΈΠΈ ΡΠΏΡΡΠ³ΠΎΠΉ ΡΠΈΡΡΠ΅ΠΌΡ Π½Π° ΡΠΎΡΠ½ΠΎΡΡΡ ΠΎΠ±ΡΠ°Π±ΠΎΡΠΊΠΈ.
ΠΠ° ΠΎΡΠ½ΠΎΠ²Π΅ Π΄Π²ΡΡ
ΠΌΠ΅ΡΠ½ΠΎΠΉ ΠΌΠΎΠ΄Π΅Π»ΠΈ ΡΠΌΠ°Π·ΠΎΡΠ½ΠΎΠ³ΠΎ ΠΏΠΎΡΠΎΠΊΠ° ΡΠ°Π·ΡΠ°Π±ΠΎΡΠ°Π½Π° ΠΌΠ°ΡΠ΅ΠΌΠ°ΡΠΈΡΠ΅ΡΠΊΠ°Ρ ΠΌΠΎΠ΄Π΅Π»Ρ,
ΠΌΠ΅ΡΠΎΠ΄ ΠΈ ΠΌΠ΅ΡΠΎΠ΄ΠΈΠΊΠ° ΡΠ°ΡΡΠ΅ΡΠ° Π½Π΅ΡΡΡΠ΅ΠΉ ΡΠΏΠΎΡΠΎΠ±Π½ΠΎΡΡΠΈ ΠΈ ΡΠ°ΡΡ
ΠΎΠ΄Π° ΡΠΌΠ°Π·ΠΊΠΈ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠ°. Π£ΡΡΠ°Π½ΠΎΠ²Π»Π΅Π½ΠΎ,
ΡΡΠΎ ΡΠ°ΡΡΠ΅Ρ ΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΈΡ
Ρ
Π°ΡΠ°ΠΊΡΠ΅ΡΠΈΡΡΠΈΠΊ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠ° Π²ΠΎ Π²ΡΠ΅ΠΌ Π΄ΠΈΠ°ΠΏΠ°Π·ΠΎΠ½Π΅ Π΄Π΅ΠΉΡΡΠ²ΡΡΡΠΈΡ
Π½Π°Π³ΡΡΠ·ΠΎΠΊ ΠΌΠΎΠΆΠ΅Ρ Π±ΡΡΡ ΠΊΠΎΡΡΠ΅ΠΊΡΠ½ΠΎ Π²ΡΠΏΠΎΠ»Π½Π΅Π½ ΡΠΎΠ»ΡΠΊΠΎ Π½Π° ΠΎΡΠ½ΠΎΠ²Π΅ Π΄Π²ΡΡ
ΠΌΠ΅ΡΠ½ΠΎΠΉ ΠΌΠΎΠ΄Π΅Π»ΠΈ. ΠΡΠΈ ΠΌΠ°Π»ΡΡ
ΡΠΊΡΡΠ΅Π½ΡΡΠΈΡΠΈΡΠ΅ΡΠ°Ρ
Ρ
Π°ΡΠ°ΠΊΡΠ΅ΡΠΈΡΡΠΈΠΊΠΈ Π½ΡΠ»Π΅Π²ΠΎΠΉ ΠΈ ΠΎΡΡΠΈΡΠ°ΡΠ΅Π»ΡΠ½ΠΎΠΉ ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΠΈ ΠΌΠΎΠ³ΡΡ Π±ΡΡΡ
Ρ ΡΠ΄ΠΎΠ²Π»Π΅ΡΠ²ΠΎΡΠΈΡΠ΅Π»ΡΠ½ΠΎΠΉ ΡΠΎΡΠ½ΠΎΡΡΡΡ ΡΠ°ΡΡΡΠΈΡΠ°Π½Ρ ΠΏΠΎ ΡΠΏΡΠΎΡΠ΅Π½Π½ΠΎΠΉ ΠΌΠ΅ΡΠΎΠ΄ΠΈΠΊΠ΅, Π±Π°Π·ΠΈΡΡΡΡΠ΅ΠΉΡΡ
Π½Π° ΠΎΠ΄Π½ΠΎΠΌΠ΅ΡΠ½ΠΎΠΌ Π΄Π²ΠΈΠΆΠ΅Π½ΠΈΠΈ ΡΠΌΠ°Π·ΠΎΡΠ½ΠΎΠ³ΠΎ ΠΏΠΎΡΠΎΠΊΠ°. ΠΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠΈ Π½ΡΠ»Π΅Π²ΠΎΠΉ ΠΈ ΠΎΡΡΠΈΡΠ°ΡΠ΅Π»ΡΠ½ΠΎΠΉ
ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΠΈ ΠΎΠ±Π»Π°Π΄Π°ΡΡ Π³ΡΡΠ·ΠΎΠΏΠΎΠ΄ΡΠ΅ΠΌΠ½ΠΎΡΡΡΡ, ΠΊΠΎΡΠΎΡΠ°Ρ Π½Π° 20 - 50 % Π±ΠΎΠ»ΡΡΠ΅, ΡΠ΅ΠΌ Ρ ΠΎΠ±ΡΡΠ½ΡΡ
ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠΎΠ² ΡΠ΅Ρ
ΠΆΠ΅ Π³Π°Π±Π°ΡΠΈΡΠ½ΡΡ
ΡΠ°Π·ΠΌΠ΅ΡΠΎΠ². ΠΠ°ΡΡΡΠΎΠΉΠΊΠ° Π³ΠΈΠ΄ΡΠ°Π²Π»ΠΈΡΠ΅ΡΠΊΠΎΠ³ΠΎ ΡΠΎΠΏΡΠΎΡΠΈΠ²Π»Π΅Π½ΠΈΡ
Π²Ρ
ΠΎΠ΄Π½ΠΎΠΉ ΠΏΠΈΡΠ°ΡΡΠ΅ΠΉ ΡΠ΅Π»ΠΈ ΡΠ΅ΡΠ°ΡΡΠΈΠΌ ΠΎΠ±ΡΠ°Π·ΠΎΠΌ Π²Π»ΠΈΡΠ΅Ρ Π½Π° ΠΎΠΏΡΠΈΠΌΠ°Π»ΡΠ½ΡΠ΅ ΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΈΠ΅
Ρ
Π°ΡΠ°ΠΊΡΠ΅ΡΠΈΡΡΠΈΠΊΠΈ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠ°. ΠΠΏΡΠΈΠΌΠ°Π»ΡΠ½ΡΠ΅ Π·Π½Π°ΡΠ΅Π½ΠΈΡ ΡΠΎΠΏΡΠΎΡΠΈΠ²Π»Π΅Π½ΠΈΡ ΡΠ΅Π»ΠΈ Π΄Π»Ρ ΠΎΠ±ΡΡΠ½ΡΡ
ΠΈ
Π°ΠΊΡΠΈΠ²Π½ΡΡ
ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠΎΠ² ΠΏΡΠ°ΠΊΡΠΈΡΠ΅ΡΠΊΠΈ ΡΠΎΠ²ΠΏΠ°Π΄Π°ΡΡ
Characteristics of Radial Gas-Static Bearing of Step Type
Π Π°ΡΡΠΌΠΎΡΡΠ΅Π½Π° ΠΊΠΎΠ½ΡΡΡΡΠΊΡΠΈΡ ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½ΠΎΠ³ΠΎ Π³Π°Π·ΠΎΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΎΠ³ΠΎ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠ° ΡΡΡΠΏΠ΅Π½ΡΠ°ΡΠΎΠ³ΠΎ
ΡΠΈΠΏΠ°. Π ΡΡΠ°Π²Π½Π΅Π½ΠΈΠΈ Ρ ΡΡΠ°Π΄ΠΈΡΠΈΠΎΠ½Π½ΡΠΌΠΈ Π΄ΡΠΎΡΡΠ΅Π»ΡΠ½ΡΠΌΠΈ Π³Π°Π·ΠΎΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΈΠΌΠΈ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠ°ΠΌΠΈ
ΡΡΡΡΠΎΠΉΡΡΠ²ΠΎ ΠΎΡΠ»ΠΈΡΠ°Π΅ΡΡΡ ΠΏΡΠΎΡΡΠΎΡΠΎΠΉ ΠΊΠΎΠ½ΡΡΡΡΠΊΡΠΈΠΈ ΠΈ ΡΠ΅Ρ
Π½ΠΎΠ»ΠΎΠ³ΠΈΡΠ½ΠΎΡΡΡΡ. ΠΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊ Π²ΡΠ΅Π³Π΄Π°
ΡΡΡΠΎΠΉΡΠΈΠ². Π£ΠΌΠ΅Π½ΡΡΠ΅Π½ΠΈΠ΅ ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΠΈ Π½Π΅ΡΡΡΠ΅Π³ΠΎ ΡΠ»ΠΎΡ, ΠΊΠ°ΠΊ ΠΏΡΠ°Π²ΠΈΠ»ΠΎ, ΡΠΎΠΏΡΠΎΠ²ΠΎΠΆΠ΄Π°Π΅ΡΡΡ ΡΠΎΡΡΠΎΠΌ
Π±ΡΡΡΡΠΎΠ΄Π΅ΠΉΡΡΠ²ΠΈΡ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠ°. ΠΠ°Π²ΠΈΡΠΈΠΌΠΎΡΡΠΈ ΡΡΠ΅ΠΏΠ΅Π½ΠΈ ΡΡΡΠΎΠΉΡΠΈΠ²ΠΎΡΡΠΈ ΠΏΠΎ ΡΡΠ΄Ρ ΠΏΠ°ΡΠ°ΠΌΠ΅ΡΡΠΎΠ²
ΠΈΠΌΠ΅ΡΡ Π³Π»ΠΎΠ±Π°Π»ΡΠ½ΡΠΉ ΠΌΠ°ΠΊΡΠΈΠΌΡΠΌ, ΡΡΠΎ ΠΏΠΎΠ·Π²ΠΎΠ»ΡΠ΅Ρ, ΠΎΡΠ½ΠΎΠ²ΡΠ²Π°ΡΡΡ Π½Π° Π΄ΠΈΠ½Π°ΠΌΠΈΡΠ΅ΡΠΊΠΈΡ
ΡΠ°ΡΡΠ΅ΡΠ°Ρ
,
ΠΏΡΠΎΠ΅ΠΊΡΠΈΡΠΎΠ²Π°ΡΡ ΠΎΠΏΡΠΈΠΌΠ°Π»ΡΠ½ΡΠ΅ ΠΏΠΎ Π±ΡΡΡΡΠΎΠ΄Π΅ΠΉΡΡΠ²ΠΈΡ ΠΊΠΎΠ½ΡΡΡΡΠΊΡΠΈΠΈThe design of step gas-static bearing is considered. In comparison with conventional throttle gasstatic
bearings the device is characterized by simplicity of design and manufacturability. Bearing is
always stable. Decrease of compliance of the carrier gap is accompanied by increase of speed of the
bearing. Dependencies of degree of stability in a number of parameters have a global maximum, what
allows design optimal constructions based on dynamic calculation
Stability of Energy-Saving Adaptive Journal Hydrostatic Bearing with a Restriction of the Output Lubricant Stream
Π ΡΠ°Π±ΠΎΡΠ΅ ΡΠ°ΡΡΠΌΠΎΡΡΠ΅Π½Ρ Π²ΠΎΠΏΡΠΎΡΡ ΠΊΠ°ΡΠ΅ΡΡΠ²Π° Π΄ΠΈΠ½Π°ΠΌΠΈΠΊΠΈ Π°Π΄Π°ΠΏΡΠΈΠ²Π½ΠΎΠΉ ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½ΠΎΠΉ Π³ΠΈΠ΄ΡΠΎΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΎΠΉ
ΠΎΠΏΠΎΡΡ Ρ ΠΎΠ³ΡΠ°Π½ΠΈΡΠ΅Π½ΠΈΠ΅ΠΌ Π²ΡΡ
ΠΎΠ΄Π½ΠΎΠ³ΠΎ ΠΏΠΎΡΠΎΠΊΠ° ΡΠΌΠ°Π·ΠΊΠΈ. ΠΡΠΈΠ²Π΅Π΄Π΅Π½Π° ΠΌΠ°ΡΠ΅ΠΌΠ°ΡΠΈΡΠ΅ΡΠΊΠ°Ρ ΠΌΠΎΠ΄Π΅Π»Ρ ΠΎΠΏΠΎΡΡ,
ΠΏΠΎΠ»ΡΡΠ΅Π½Π° Π°Π½Π°Π»ΠΈΡΠΈΡΠ΅ΡΠΊΠ°Ρ Π·Π°Π²ΠΈΡΠΈΠΌΠΎΡΡΡ Π΄Π»Ρ ΠΏΠ΅ΡΠ΅Π΄Π°ΡΠΎΡΠ½ΠΎΠΉ ΡΡΠ½ΠΊΡΠΈΠΈ Π΄ΠΈΠ½Π°ΠΌΠΈΡΠ΅ΡΠΊΠΎΠΉ ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΠΈ
Π»ΠΈΠ½Π΅Π°ΡΠΈΠ·ΠΎΠ²Π°Π½Π½ΠΎΠΉ Π½Π΅ΡΡΠ°ΡΠΈΠΎΠ½Π°ΡΠ½ΠΎΠΉ ΠΌΠΎΠ΄Π΅Π»ΠΈ.
Π£ΡΡΠ°Π½ΠΎΠ²Π»Π΅Π½ΠΎ, ΡΡΠΎ ΠΎΠΏΠΎΡΠ° ΠΌΠΎΠΆΠ΅Ρ ΡΠ°Π±ΠΎΡΠ°ΡΡ ΡΡΡΠΎΠΉΡΠΈΠ²ΠΎ Π½Π° ΡΠ΅ΠΆΠΈΠΌΠ°Ρ
ΠΎΡΡΠΈΡΠ°ΡΠ΅Π»ΡΠ½ΠΎΠΉ
ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΠΈ. ΠΡΠΈ ΡΡΠΎΠΌ ΠΎΠ±Π΅ΡΠΏΠ΅ΡΠΈΠ²Π°ΡΡΡΡ ΠΏΡΠΈΠ΅ΠΌΠ»Π΅ΠΌΡΠ΅ ΠΏΠΎΠΊΠ°Π·Π°ΡΠ΅Π»ΠΈ ΠΊΠ°ΡΠ΅ΡΡΠ²Π° Π΄ΠΈΠ½Π°ΠΌΠΈΠΊΠΈ
ΡΠ²ΠΎΠ±ΠΎΠ΄Π½ΡΡ
ΠΈ Π²ΡΠ½ΡΠΆΠ΄Π΅Π½Π½ΡΡ
ΠΊΠΎΠ»Π΅Π±Π°Π½ΠΈΠΉ. Π£ΡΡΠΎΠΉΡΠΈΠ²Π°Ρ ΠΎΠΏΠΎΡΠ° ΠΈΠΌΠ΅Π΅Ρ ΠΎΠ³ΡΠ°Π½ΠΈΡΠ΅Π½Π½ΡΡ ΠΎΠ±Π»Π°ΡΡΡ
ΠΎΡΡΠΈΡΠ°ΡΠ΅Π»ΡΠ½ΠΎΠΉ ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΠΈ. ΠΠΎΠ½ΡΡΡΡΠΊΡΠΈΡ ΠΎΠΏΠΎΡΡ ΠΏΡΠΈ ΠΎΠ΄ΠΈΠ½Π°ΡΠ½ΠΎΠΌ Π΄ΡΠΎΡΡΠ΅Π»ΠΈΡΠΎΠ²Π°Π½ΠΈΠΈ Π²Ρ
ΠΎΠ΄Π½ΠΎΠ³ΠΎ
ΠΏΠΎΡΠΎΠΊΠ° ΡΠΌΠ°Π·ΠΊΠΈ ΡΠΊΠ»ΠΎΠ½Π½Π° ΠΊ ΠΊΠΎΠ»Π΅Π±Π°Π½ΠΈΡΠΌ, ΠΎΠ΄Π½Π°ΠΊΠΎ Π² ΡΠΊΠ°Π·Π°Π½Π½ΠΎΠΉ ΠΎΠ±Π»Π°ΡΡΠΈ ΠΎΠ±Π»Π°Π΄Π°Π΅Ρ Π΄ΠΎΡΡΠ°ΡΠΎΡΠ½ΡΠΌ
Π·Π°ΠΏΠ°ΡΠΎΠΌ ΡΡΡΠΎΠΉΡΠΈΠ²ΠΎΡΡΠΈ.The paper discusses issues of quality of the dynamics for adaptive radial hydrostatic bearing with
a restriction of the output lubricant stream. The article presents a mathematical model of support,
an analytical dependence for the transfer function of the dynamic compliance for the linearized
nonstationary model.
It is established that reliance can operate stably at modes of negative compliance. This provided an
acceptable quality indicators of dynamics for free and forced oscillations. Sustained bearing has a
limited region of negative compliance. Design of bearing for ordinary throttling input lubricant is
prone to fluctuations, but in this area has a sufficient margin of stability
Π§ΠΈΡΠ»Π΅Π½Π½ΠΎ-Π°Π½Π°Π»ΠΈΡΠΈΡΠ΅ΡΠΊΠΈΠΉ ΠΌΠ΅ΡΠΎΠ΄ ΠΎΠΏΡΠ΅Π΄Π΅Π»Π΅Π½ΠΈΡ ΡΡΠ°Π²Π½Π΅Π½ΠΈΠΉ ΡΠ²ΡΠ·ΠΈ Π»Π°ΠΏΠ»Π°ΡΠΎΠ²ΡΡ ΡΡΠ°Π½ΡΡΠΎΡΠΌΠ°Π½Ρ ΠΎΠ±ΠΎΠ±ΡΠ΅Π½Π½ΠΎΠ³ΠΎ ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½ΠΎΠ³ΠΎ Π±Π»ΠΎΠΊΠ° Π³Π°Π·ΠΎΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΈΡ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠΎΠ²
The paper proposes a numeric-analytical method for determining the communication equations
of Laplaceβs transformants of dynamic functions of the universal unit of radial externallypressurized
gas bearings which movable element makes small radial oscillations in the locality in
its central position. Method and obtained dependences provide links between integro-differential
Laplaceβs transformants of the unit such as load capacity and local input and output mass flow
rates with transformants of eccentricity and gas lubricant pressure at inlet and outlet of the
unit. It is shown that the local transfer functions of the unit model are rational functions of the
Laplaceβs transform variable and all such functions have a common denominator in the form of
a polynomial of this variable. The method allows to calculate the required dynamic criterion of
gas bearings containing this unit with prescribed accuracy. Founded dependences give ready
formulas for calculation dynamic criteria of radial single-row or multi-row ordinary passive or
active externally-pressurized gas bearings in which this unit can be used for description of radial
movement of its movable elementΠΡΠ΅Π΄Π»ΠΎΠΆΠ΅Π½ ΡΠΈΡΠ»Π΅Π½Π½ΠΎ-Π°Π½Π°Π»ΠΈΡΠΈΡΠ΅ΡΠΊΠΈΠΉ ΠΌΠ΅ΡΠΎΠ΄ ΠΎΠΏΡΠ΅Π΄Π΅Π»Π΅Π½ΠΈΡ Π»Π°ΠΏΠ»Π°ΡΠΎΠ²ΡΡ
ΡΡΠ°Π½ΡΡΠΎΡΠΌΠ°Π½Ρ
Π΄ΠΈΠ½Π°ΠΌΠΈΡΠ΅ΡΠΊΠΈΡ
ΡΡΠ½ΠΊΡΠΈΠΉ Π΄Π»Ρ ΡΠ½ΠΈΠ²Π΅ΡΡΠ°Π»ΡΠ½ΠΎΠ³ΠΎ ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½ΠΎΠ³ΠΎ Π±Π»ΠΎΠΊΠ° Π³Π°Π·ΠΎΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΈΡ
ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠΎΠ²,
ΠΏΠΎΠ΄Π²ΠΈΠΆΠ½ΡΠΉ ΡΠ»Π΅ΠΌΠ΅Π½Ρ ΠΊΠΎΡΠΎΡΠΎΠ³ΠΎ ΡΠΎΠ²Π΅ΡΡΠ°Π΅Ρ ΠΌΠ°Π»ΡΠ΅ ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½ΡΠ΅ ΠΊΠΎΠ»Π΅Π±Π°Π½ΠΈΡ Π² ΠΎΠΊΡΠ΅ΡΡΠ½ΠΎΡΡΠΈ Π΅Π³ΠΎ
ΡΠ΅Π½ΡΡΠ°Π»ΡΠ½ΠΎΠ³ΠΎ ΠΏΠΎΠ»ΠΎΠΆΠ΅Π½ΠΈΡ.
ΠΠ΅ΡΠΎΠ΄ ΠΈ ΠΏΠΎΠ»ΡΡΠ΅Π½Π½ΡΠ΅ Π·Π°Π²ΠΈΡΠΈΠΌΠΎΡΡΠΈ ΠΏΠΎΠ·Π²ΠΎΠ»ΡΡΡ ΡΡΡΠ°Π½ΠΎΠ²ΠΈΡΡ ΡΠ²ΡΠ·Ρ ΠΈΠ½ΡΠ΅Π³ΡΠΎ-Π΄ΠΈΡΡΠ΅ΡΠ΅Π½ΡΠΈΠ°Π»ΡΠ½ΡΡ
Π»Π°ΠΏΠ»Π°ΡΠΎΠ²ΡΡ
ΡΡΠ°Π½ΡΡΠΎΡΠΌΠ°Π½Ρ Π½Π΅ΡΡΡΠ΅ΠΉ ΡΠΏΠΎΡΠΎΠ±Π½ΠΎΡΡΠΈ ΠΈ Π»ΠΎΠΊΠ°Π»ΡΠ½ΡΡ
ΠΌΠ°ΡΡΠΎΠ²ΡΡ
ΡΠ°ΡΡ
ΠΎΠ΄ΠΎΠ² Π½Π° Π²Ρ
ΠΎΠ΄Π΅ ΠΈ
Π²ΡΡ
ΠΎΠ΄Π΅ Π±Π»ΠΎΠΊΠ° Ρ ΡΡΠ°Π½ΡΡΠΎΡΠΌΠ°Π½ΡΠ°ΠΌΠΈ ΡΠΊΡΡΠ΅Π½ΡΡΠΈΡΠΈΡΠ΅ΡΠ° ΠΈ Π΄Π°Π²Π»Π΅Π½ΠΈΠΉ ΡΠΌΠ°Π·ΡΠ²Π°ΡΡΠ΅Π³ΠΎ Π³Π°Π·Π° Π½Π° Π²Ρ
ΠΎΠ΄Π΅
ΠΈ Π²ΡΡ
ΠΎΠ΄Π΅ Π±Π»ΠΎΠΊΠ°. ΠΠΎΠΊΠ°Π·Π°Π½ΠΎ, ΡΡΠΎ Π»ΠΎΠΊΠ°Π»ΡΠ½ΡΠ΅ ΠΏΠ΅ΡΠ΅Π΄Π°ΡΠΎΡΠ½ΡΠ΅ ΡΡΠ½ΠΊΡΠΈΠΈ Π±Π»ΠΎΠΊΠ° ΠΏΡΠ΅Π΄ΡΡΠ°Π²Π»ΡΡΡ ΡΠΎΠ±ΠΎΠΉ
ΡΠ°ΡΠΈΠΎΠ½Π°Π»ΡΠ½ΡΠ΅ ΡΡΠ½ΠΊΡΠΈΠΈ ΠΏΠ΅ΡΠ΅ΠΌΠ΅Π½Π½ΠΎΠΉ ΠΏΡΠ΅ΠΎΠ±ΡΠ°Π·ΠΎΠ²Π°Π½ΠΈΡ ΠΠ°ΠΏΠ»Π°ΡΠ° ΠΈ ΡΡΠΎ Π²ΡΠ΅ ΡΠ°ΠΊΠΈΠ΅ ΡΡΠ½ΠΊΡΠΈΠΈ ΠΈΠΌΠ΅ΡΡ
ΠΎΠ±ΡΠΈΠΉ Π·Π½Π°ΠΌΠ΅Π½Π°ΡΠ΅Π»Ρ Π² Π²ΠΈΠ΄Π΅ ΠΏΠΎΠ»ΠΈΠ½ΠΎΠΌΠ° ΠΎΡΠ½ΠΎΡΠΈΡΠ΅Π»ΡΠ½ΠΎ ΡΡΠΎΠΉ ΠΏΠ΅ΡΠ΅ΠΌΠ΅Π½Π½ΠΎΠΉ.
ΠΠ΅ΡΠΎΠ΄ ΠΏΠΎΠ·Π²ΠΎΠ»ΡΠ΅Ρ Π²ΡΡΠΈΡΠ»ΡΡΡ ΡΡΠ΅Π±ΡΠ΅ΠΌΡΠΉ ΠΊΡΠΈΡΠ΅ΡΠΈΠΉ ΠΊΠ°ΡΠ΅ΡΡΠ²Π° Π΄ΠΈΠ½Π°ΠΌΠΈΠΊΠΈ ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠΎΠ²,
ΡΠΎΠ΄Π΅ΡΠΆΠ°ΡΠΈΡ
Π΄Π°Π½Π½ΡΠΉ Π±Π»ΠΎΠΊ, Ρ Π½Π°ΠΏΠ΅ΡΠ΅Π΄ Π·Π°Π΄Π°Π½Π½ΠΎΠΉ ΡΠΎΡΠ½ΠΎΡΡΡΡ.
ΠΠ°ΠΉΠ΄Π΅Π½Π½ΡΠ΅ ΡΡΠ°Π²Π½Π΅Π½ΠΈΡ ΡΠ²ΡΠ·Π΅ΠΉ Π΄Π°ΡΡ Π³ΠΎΡΠΎΠ²ΡΠ΅ ΡΠΎΡΠΌΡΠ»Ρ Π΄Π»Ρ ΡΠ°ΡΡΠ΅ΡΠ° ΠΊΡΠΈΡΠ΅ΡΠΈΠ΅Π² ΠΊΠ°ΡΠ΅ΡΡΠ²Π°
Π΄ΠΈΠ½Π°ΠΌΠΈΠΊΠΈ ΡΠΎΠ΄Π΅ΡΠΆΠ°ΡΠΈΡ
ΡΠ°ΠΊΠΎΠΉ Π±Π»ΠΎΠΊ ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½ΡΡ
ΠΎΠ΄Π½ΠΎΡΡΠ΄Π½ΡΡ
, ΠΌΠ½ΠΎΠ³ΠΎΡΡΠ΄Π½ΡΡ
ΠΎΠ±ΡΡΠ½ΡΡ
ΠΏΠ°ΡΡΠΈΠ²Π½ΡΡ
ΠΈΠ»ΠΈ Π°ΠΊΡΠΈΠ²Π½ΡΡ
Π³Π°Π·ΠΎΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΈΡ
ΠΏΠΎΠ΄ΡΠΈΠΏΠ½ΠΈΠΊΠΎΠ², Π² ΠΊΠΎΡΠΎΡΡΡ
ΡΠΎΠ²Π΅ΡΡΠ°Π΅ΡΡΡ ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½ΠΎΠ΅ Π΄Π²ΠΈΠΆΠ΅Π½ΠΈΠ΅
ΠΈΡ
ΠΏΠΎΠ΄Π²ΠΈΠΆΠ½ΡΡ
ΡΠ»Π΅ΠΌΠ΅Π½ΡΠΎ
Negative Compliance of Energy-Saving Adaptive Journal Hydrostatic Bearing with a Restriction of the Output Lubricant Stream
ΠΠ΅ΡΠΊΠΎΠ½ΡΠ°ΠΊΡΠ½ΡΠ΅ ΠΎΠΏΠΎΡΡ ΡΠΊΠΎΠ»ΡΠΆΠ΅Π½ΠΈΡ Ρ ΠΆΠΈΠ΄ΠΊΠΎΡΡΠ½ΠΎΠΉ ΡΠΌΠ°Π·ΠΊΠΎΠΉ, ΠΎΠ±Π»Π°Π΄Π°ΡΡΠΈΠ΅ ΠΎΡΡΠΈΡΠ°ΡΠ΅Π»ΡΠ½ΠΎΠΉ
ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΡΡ Π½Π΅ΡΡΡΠ΅Π³ΠΎ ΡΠΌΠ°Π·ΠΎΡΠ½ΠΎΠ³ΠΎ ΡΠ»ΠΎΡ, ΠΌΠΎΠ³ΡΡ Π±ΡΡΡ ΠΈΡΠΏΠΎΠ»ΡΠ·ΠΎΠ²Π°Π½Ρ Π² ΡΠ·Π»Π°Ρ
ΡΡΠ°Π½ΠΊΠΎΠ² Π΄Π»Ρ
ΠΊΠΎΠΌΠΏΠ΅Π½ΡΠ°ΡΠΈΠΈ Π΄Π΅ΡΠΎΡΠΌΠ°ΡΠΈΠΉ Π΅Π³ΠΎ ΡΠΏΡΡΠ³ΠΎΠΉ ΡΠΈΡΡΠ΅ΠΌΡ Ρ ΡΠ΅Π»ΡΡ ΠΏΠΎΠ²ΡΡΠ΅Π½ΠΈΡ ΡΠΎΡΠ½ΠΎΡΡΠΈ ΠΎΠ±ΡΠ°Π±ΠΎΡΠΊΠΈ.
ΠΠ·Π²Π΅ΡΡΠ½ΡΠ΅ ΠΊΠΎΠ½ΡΡΡΡΠΊΡΠΈΠΈ ΡΠ°ΠΊΠΈΡ
ΠΎΠΏΠΎΡ, Π² ΠΊΠΎΡΠΎΡΡΡ
ΡΠΌΠ΅Π½ΡΡΠ΅Π½ΠΈΠ΅ ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΠΈ ΠΏΡΠΎΠΈΡΡ
ΠΎΠ΄ΠΈΡ Π·Π°
ΡΡΠ΅Ρ ΠΏΡΠΈΠΌΠ΅Π½Π΅Π½ΠΈΡ Π²Ρ
ΠΎΠ΄Π½ΡΡ
ΡΠ΅Π³ΡΠ»ΡΡΠΎΡΠΎΠ² ΡΠ°ΡΡ
ΠΎΠ΄Π° (ΠΠΠ‘Π-Π Π ), ΠΎΠ±Π»Π°Π΄Π°ΡΡ Π²ΡΡΠΎΠΊΠΎΠΉ ΡΠ½Π΅ΡΠ³ΠΎΠ΅ΠΌΠΊΠΎΡΡΡΡ
ΠΈ Π½Π΅ΡΡΠ°Π±ΠΈΠ»ΡΠ½ΠΎΡΡΡΡ Ρ
Π°ΡΠ°ΠΊΡΠ΅ΡΠΈΡΡΠΈΠΊΠΈ ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΠΈ. Π Π½Π°ΡΡΠΎΡΡΠ΅ΠΉ ΡΠ°Π±ΠΎΡΠ΅ ΡΠ°ΡΡΠΌΠΎΡΡΠ΅Π½Π°
ΠΊΠΎΠ½ΡΡΡΡΠΊΡΠΈΡ Π½ΠΎΠ²ΠΎΠΉ ΠΊΠ°ΡΠ΅Π³ΠΎΡΠΈΠΈ Π°Π΄Π°ΠΏΡΠΈΠ²Π½ΡΡ
ΠΎΠΏΠΎΡ - ΡΠ°Π΄ΠΈΠ°Π»ΡΠ½Π°Ρ Π³ΠΈΠ΄ΡΠΎΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠ°Ρ ΠΎΠΏΠΎΡΠ° Ρ
ΠΎΠ³ΡΠ°Π½ΠΈΡΠ΅Π½ΠΈΠ΅ΠΌ Π²ΡΡ
ΠΎΠ΄Π½ΠΎΠ³ΠΎ ΠΏΠΎΡΠΎΠΊΠ° ΡΠΌΠ°Π·ΠΊΠΈ (ΠΠΠ‘Π-ΠΠ). ΠΡΠΈΠ²Π΅Π΄Π΅Π½Π° ΠΌΠ°ΡΠ΅ΠΌΠ°ΡΠΈΡΠ΅ΡΠΊΠ°Ρ ΠΌΠΎΠ΄Π΅Π»Ρ
ΠΎΠΏΠΎΡΡ, ΠΏΠΎΠ»ΡΡΠ΅Π½Ρ ΡΠ°ΡΡΠ΅ΡΠ½ΡΠ΅ Π°Π½Π°Π»ΠΈΡΠΈΡΠ΅ΡΠΊΠΈΠ΅ Π·Π°Π²ΠΈΡΠΈΠΌΠΎΡΡΠΈ ΠΈ ΡΠ°ΡΡΠΌΠΎΡΡΠ΅Π½ ΡΠΏΡΠΎΡΠ΅Π½Π½ΡΠΉ ΠΌΠ΅ΡΠΎΠ΄
ΠΎΠΏΡΠ΅Π΄Π΅Π»Π΅Π½ΠΈΡ Π΅Ρ ΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΈΡ
Ρ
Π°ΡΠ°ΠΊΡΠ΅ΡΠΈΡΡΠΈΠΊ Π±Π΅Π· ΡΡΠ΅ΡΠ° Π²Π»ΠΈΡΠ½ΠΈΡ Π½Π° Π½ΠΈΡ
ΠΎΠΊΡΡΠΆΠ½ΡΡ
ΠΏΠ΅ΡΠ΅ΡΠΎΠΊΠΎΠ²
ΡΠΌΠ°Π·ΠΊΠΈ. ΠΠΎΠΊΠ°Π·Π°Π½ΠΎ, ΡΡΠΎ ΠΠΠ‘Π-ΠΠ Π² ΡΡΠ°Π²Π½Π΅Π½ΠΈΠΈ Ρ ΠΠΠ‘Π-Π Π ΠΏΠΎΡΡΠ΅Π±Π»ΡΠ΅Ρ ΡΠ½Π΅ΡΠ³ΠΈΠΈ Π² 3-4 ΡΠ°Π·Π°
ΠΌΠ΅Π½ΡΡΠ΅. ΠΡΠΈ ΡΡΠΎΠΌ ΠΎΠ½Π° ΠΎΠ±Π»Π°Π΄Π°Π΅Ρ Π±ΠΎΠ»Π΅Π΅ ΡΡΠ°Π±ΠΈΠ»ΡΠ½ΡΠΌΠΈ Ρ
Π°ΡΠ°ΠΊΡΠ΅ΡΠΈΡΡΠΈΠΊΠ°ΠΌΠΈ ΠΎΡΡΠΈΡΠ°ΡΠ΅Π»ΡΠ½ΠΎΠΉ
ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΠΈ ΠΈ Π±ΠΎΠ»Π΅Π΅ ΡΠΈΡΠΎΠΊΠΈΠΌ Π°Π΄Π°ΠΏΡΠΈΠ²Π½ΡΠΌ Π΄ΠΈΠ°ΠΏΠ°Π·ΠΎΠ½ΠΎΠΌ Π½Π°Π³ΡΡΠ·ΠΎΠΊ. Π£ΡΡΠ°Π½ΠΎΠ²Π»Π΅Π½ΠΎ ΡΠ°ΠΊΠΆΠ΅,
ΡΡΠΎ ΠΠΠ‘Π-ΠΠ ΠΎΡΡΠΈΡΠ°ΡΠ΅Π»ΡΠ½ΠΎΠΉ ΠΏΠΎΠ΄Π°ΡΠ»ΠΈΠ²ΠΎΡΡΠΈ Π±ΠΎΠ»Π΅Π΅ ΡΠΊΠΎΠ½ΠΎΠΌΠΈΡΠ½Π° Π΄Π°ΠΆΠ΅ Π² ΡΡΠ°Π²Π½Π΅Π½ΠΈΠΈ Ρ ΠΎΠ±ΡΡΠ½ΠΎΠΉ
Π³ΠΈΠ΄ΡΠΎΡΡΠ°ΡΠΈΡΠ΅ΡΠΊΠΎΠΉ ΠΎΠΏΠΎΡΠΎΠΉ.Non-contact sliding bearings lubricated with a liquid, which have a negative compliance of lubricating
film, can be used in the machine-tool nodes to compensate of its elastic system deformation for improve
the accuracy of processing. Known designs of such bearings, in which a decrease in ductility is due
to the application of input consumption regulators (AGSB-CR), have high energy costs and instability
characteristics of compliance. In this paper we consider the construction of a new category of adaptive
bearings - journal hydrostatic bearing with a restriction of the output lubricant stream (AGSB-OS).
The paper presents a mathematical model of support, according to analytical estimates obtained and
considered a simplified method for determination of its static characteristics without the influence on
them district overflows lubrication. It is shown that AGSB-OS compared with AGSB-CR consumes
energy is 3-4 times smaller. It has more stable characteristics of negative compliance and a broader
range of adaptive loads. It was also found that AGSB-OS with negative compliance is more economical,
even in comparison with the conventional hydrostatic bearing